CN102341623A

CN102341623A - Medium pressure control device of continuously variable transmission and continuously variable transmission

Info

Publication number: CN102341623A
Application number: CN2009801579220A
Authority: CN
Inventors: 伊藤良雄
Original assignee: Toyota Motor Corp
Current assignee: Toyota Motor Corp
Priority date: 2009-03-27
Filing date: 2009-03-27
Publication date: 2012-02-01
Anticipated expiration: 2029-03-27
Also published as: WO2010109654A1; CN102341623B; US20120040792A1; JPWO2010109654A1; JP5556807B2; US9091344B2

Abstract

A medium pressure control device of a continuously variable transmission includes a pump unit capable of switching a discharge volume of an operating medium to a control system, which controls a contacting surface pressure of rotation members and a transmitting member and the transmission ratio by a pressure of the operating medium, in plural stages; and a transmission ratio control unit that controls the control system and relatively delays a transmission shift when the discharge volume of the operating medium to the control system by the pump unit switches from a relatively small volume to a relatively large volume with the transmission shift.

Description

The pressure medium control gear and the stepless speed variator of stepless speed variator

Technical field

The present invention relates to the pressure medium control gear and the stepless speed variator of stepless speed variator, relate to particularly with the corresponding optimum condition of the travelling state of vehicle under from as the internal-combustion engine of driving source or motor pressure medium control gear and stepless speed variator to the stepless speed variator of road surface transmission of drive force.

Background technique

Usually, vehicle is provided with speed changer at the outlet side of driving source, with the corresponding optimum condition of the travelling state of vehicle under from as the internal-combustion engine of driving source or motor to the road surface transmission of drive force, promptly export torque.In this speed changer, have infinitely the stepless speed variator of (continuously) control gear ratio and the step change transmission that control gear ratio in level ground (discontinuously) is arranged.Here, at such stepless speed variator, so-called CVT (CVT: stepless speed variator), for example have so-called toroidal continuously variable transmission or variable v-belt drive etc.Toroidal continuously variable transmission is via being clipped in as the input disk of the rotary component of input side and as the live roll transmitting torque between each disk as transferring elements between the output disk of the rotary component of outlet side, and live roll verted change gear ratio.Variable v-belt drive comprises primary pulley, secondary pulley and band; And gear ratio is changed through the contact radius that changes band and belt wheel; Primary pulley is the rotary component that is passed to input side wherein from drive source drives power; Secondary pulley is the driving force that is delivered to primary pulley to be changed and with the rotary component of the outlet side of its output, band is the transferring elements that the driving force that is delivered to this primary pulley is transmitted to secondary pulley.

For example; This toroidal continuously variable transmission is clamped the rotary units such as live roll of outer circumferential face as the curved surface corresponding with ring surface between input disk with ring surface and output disk, and is utilized in the shearing transmitting torque of the oil film of the traction that forms between these input disk, output disk and live rolls.And; But this live roll is by the gudgeon free rotary ground supporting; This gudgeon can be the center rotation with the running shaft; And for example through as the oil pressure of the working oil of the working medium that is supplied to speed Control hydraulic chamber (speed Control pressure chamber) to being arranged on the piston action speed Control pressing force on the gudgeon, thereby can move to direction along this running shaft.

Therefore; Through by the live roll of gudgeon supporting with this gudgeon from moving to shift position with respect to the neutral position of input disk and output disk, break away thereby tangential force acts on to produce between live roll and the disk, this live roll is the center rotation with the running shaft with respect to input disk and output disk; Promptly; This live roll verts, and consequently, the rotating ratio of input disk and output disk is that gear ratio changes.And; The angle of verting with respect to input disk and output disk based on live roll is that tilt angle is confirmed the gear ratio as the rotating ratio of input disk and output disk, and based on as this live roll from the neutral position integral value to the path increment (side-play amount) of the amount of movement of shift position side confirm this tilt angle.

In addition; Such toroidal continuously variable transmission for example is used between input disk and output disk, clamping the predetermined clamping pressure of live roll through the effect of cramping unit; Come in the contact segment of input disk, output disk and live roll, to regulate surface of contact and press, thereby keep suitable traction state.And; Such cramping unit for example acts on the pressure acting surface through the pressure as the working oil of working medium that will be supplied to clamping pressure to produce hydraulic chamber (surface of contact pressure-controlled pressure chamber), thereby effect is clipped in the clamping pressure between input disk and the output disk with live roll.

In addition, also be provided with such hydraulic type cramping unit in the above-mentioned variable v-belt drive.Promptly; Variable v-belt drive acts on the pressure acting surface through making the pressure as the working oil of working medium that is supplied to clamping pressure to produce hydraulic chamber (surface of contact pressure-controlled pressure chamber); Push movable sheave to the fixed pulley side, thus, the strap clamp pressure of band is clamped in effect between movable sheave and fixed pulley; Adjusting belt tension force is regulated surface of contact and is pressed in the contact segment of belt wheel and band.

Pressure medium control gear for so existing stepless speed variator; For example; The hydraulic pressure control device of the stepless speed variator of record is supplied to pipeline (for example to press the supply destination through the ejection oil separately that bleed off circuit is closed first and second oil pump when the urgent speed change in the patent documentation 1; Speed Control pressure chamber or surface of contact pressure-controlled pressure chamber) thus suppress pipeline and press supply destination oil starvation; On the other hand; Through being communicated with the ejection oral-lateral of first oil pump and the suction oral-lateral of second oil pump in the time except that urgent speed change by bleed off circuit, second oil pump utilizes the ejection oil of the high pressure in first oil pump to come to suck efficiently working oil and reduces pump and drives loss, thereby uses first and second oil pump efficiently.

[patent documentation 1] spy opens the 2005-221047 communique

Summary of the invention

Problem to be solved by this invention

Yet; In the hydraulic pressure control device of the stepless speed variator of in patent documentation 1, putting down in writing; For example, even be supplied to pipeline and press under the situation of the state of supplying the destination being supplied to state transformation that pipeline presses supply destination (for example, speed Control pressure chamber or surface of contact pressure-controlled pressure chamber) ejection oil separately from the ejection oil of second oil pump only to first and second oil pump; According to running state; Pipeline is pressed the supply destination working oil deficiency that also possibly become, and therefore, the conversion according to the ejection capacity of the more suitable oil pump of running state is carried out in expectation.

Therefore, the purpose of this invention is to provide can be according to running state suitably the pressure medium control gear and the stepless speed variator of the stepless speed variator of the ejection capacity of conversion working medium.

The means that are used to deal with problems

To achieve these goals; The present invention provides the pressure medium control gear of stepless speed variator; Said stepless speed variator can pass to from the rotary component of input side driving force the rotary component of outlet side via transferring elements; And can infinitely change gear ratio; Said gear ratio is the said rotary component of input side and the rotational speed ratio of the said rotary component of outlet side, and said pressure medium control gear is characterised in that, comprising: the pump unit; Said pump unit can multistage ground conversion working medium to the ejection capacity of control system, the surface of contact that said control system is controlled between said rotary component and the said transferring elements through the pressure of said working medium is pressed and said gear ratio; And gear ratio control unit; When the ejection capacity that sprays said working medium to said control system through said pump unit along with speed change when relatively little capacity transforms to big relatively capacity, said gear ratio control unit is controlled said control system and said speed change is relatively delayed.

In addition; In the pressure medium control gear of above-mentioned stepless speed variator; Also can constitute when the ejection capacity that sprays said working medium to said control system through said pump unit along with speed change when relatively little capacity transforms to big relatively capacity, said gear ratio control unit is controlled said control system and the speed change speed of said speed change is relatively descended.

In addition; In the pressure medium control gear of above-mentioned stepless speed variator; Also can constitute when the ejection capacity that sprays said working medium to said control system through said pump unit along with speed change when relatively little capacity transforms to big relatively capacity, said gear ratio control unit is controlled said control system and the elapsed time point of said speed change is relatively delayed.

In addition; In the pressure medium control gear of above-mentioned stepless speed variator; Also can constitute said gear ratio control unit begun to transform to from the conversion of the ejection capacity of said pump unit to the ejection capacity of the reality of said pump unit said big relatively capacity during, said speed change is delayed.

In addition; In the pressure medium control gear of above-mentioned stepless speed variator; Also can constitute and comprise the conversion control unit; When said gear ratio control unit was controlled said control system and said speed change is delayed, said conversion control unit was controlled said pump unit and is relatively increased the conversion rate of said working medium to the ejection capacity of said control system.

In addition, in the pressure medium control gear of above-mentioned stepless speed variator, also can constitute said pump unit and have: first pump, said first pump sprays said working medium to said control system; Second pump, said second pump sprays said working medium to the supply system that said control system perhaps is different from said control system; And converter unit, said converter unit can be between said control system and said supply system the ejection destination of the said working medium in said second pump of conversion.

In addition; In the pressure medium control gear of above-mentioned stepless speed variator; Also can constitute said control system comprises: gear ratio changes the unit, and the pressure that said gear ratio changes the said working medium of unit through being supplied to the speed Control pressure chamber changes said gear ratio; And surface of contact press to change the unit, and said surface of contact is pressed the pressure that changes the said working medium of unit through being supplied to surface of contact pressure-controlled pressure chamber to change said surface of contact and pressed.

To achieve these goals, stepless speed variator of the present invention is characterised in that, comprising: the pressure medium control gear of above-mentioned stepless speed variator; And the live roll that constitutes said transferring elements.

To achieve these goals, stepless speed variator of the present invention is characterised in that, comprising: the pressure medium control gear of above-mentioned stepless speed variator; And the band that constitutes said transferring elements.

The invention effect

According to the pressure medium control gear of the stepless speed variator that the present invention relates to, can be according to the running state ejection capacity of conversion working medium suitably.

According to the stepless speed variator that the present invention relates to, can be according to the running state ejection capacity of conversion working medium suitably.

Description of drawings

Fig. 1 is the concise and to the point pie graph of the related hydraulic pressure control device of mode of execution of the present invention;

Fig. 2 is the concise and to the point pie graph of power-transmission system that the vehicle of the toroidal continuously variable transmission of having used the hydraulic pressure control device that mode of execution of the present invention relates to is installed.

Fig. 3 is a concise and to the point sectional drawing of having used the toroidal continuously variable transmission of the hydraulic pressure control device that mode of execution of the present invention relates to;

Fig. 4 is the pie graph of pattern of major component of having used the toroidal continuously variable transmission of the hydraulic pressure control device that mode of execution of the present invention relates to;

Fig. 5 is that the ideograph of the included live roll of the toroidal continuously variable transmission of the hydraulic pressure control device that mode of execution of the present invention relates to respect to the neutral position of input disk used in explanation;

Fig. 6 is that the ideograph of the included live roll of the toroidal continuously variable transmission of the hydraulic pressure control device that mode of execution of the present invention relates to respect to the shift position of input disk used in explanation;

Fig. 7 is the figure of the conversion of the ejection capacity in the hydraulic pressure control device that relates to of explanation mode of execution of the present invention;

Fig. 8 is the flow chart of conversion control of ejection capacity of the pump-unit of the hydraulic pressure control device that relates to of explanation mode of execution of the present invention;

Fig. 9 is the sequential chart of an example of conversion control of ejection capacity of the pump-unit of the hydraulic pressure control device that relates to of explanation mode of execution of the present invention;

Figure 10 is a concise and to the point pie graph of having used the variable v-belt drive of the hydraulic pressure control device that variation of the present invention relates to.

Label declaration

1: toroidal continuously variable transmission (stepless speed variator)

1A: vehicle

2: input disk (rotary component of input side)

3: output disk (rotary component of outlet side)

4: live roll (transferring elements)

5: gear ratio change portion (gear ratio change unit)

9: hydraulic pressure control device (pressure medium control gear)

15: oil pressure pressing mechanism (surface of contact is pressed and changed the unit)

15a: clamping pressure produces hydraulic chamber (surface of contact pressure-controlled pressure chamber)

65: gear ratio control device (gear ratio control unit)

66: conversion control device (conversion control unit)

82: speed Control hydraulic chamber (speed Control pressure chamber)

90A: control system

90B: lubrication system (supply system)

91: food tray

92: pump-unit (pump unit)

96: main pump (first pump)

97: auxiliary pump (second pump)

98: transfer valve (converter unit)

101: variable v-belt drive (stepless speed variator)

102: primary pulley (rotary component of input side, gear ratio changes the unit)

103: secondary pulley (rotary component of outlet side, surface of contact are pressed and changed the unit)

104: band (transferring elements)

124: elementary hydraulic chamber (speed Control pressure chamber)

134: secondary hydraulic chamber (surface of contact pressure-controlled pressure chamber)

Embodiment

Below, based on accompanying drawing the pressure medium control gear of the stepless speed variator that the present invention relates to and the mode of execution of stepless speed variator are elaborated.In addition, the invention is not restricted to this mode of execution.In addition, the constituting component in the following mode of execution comprises parts or the identical parts of essence that those skilled in the art can and replace easily.

(mode of execution)

Fig. 1 is the concise and to the point pie graph of the hydraulic pressure control device that relates to of mode of execution of the present invention; Fig. 2 is the concise and to the point pie graph of power-transmission system that the vehicle of the toroidal continuously variable transmission of having used the hydraulic pressure control device that mode of execution of the present invention relates to is installed; Fig. 3 is a concise and to the point sectional drawing of having used the toroidal continuously variable transmission of the hydraulic pressure control device that mode of execution of the present invention relates to; Fig. 4 is the pie graph of pattern of major component of having used the toroidal continuously variable transmission of the hydraulic pressure control device that mode of execution of the present invention relates to; Fig. 5 is that the ideograph of the included live roll of the toroidal continuously variable transmission of the hydraulic pressure control device that mode of execution of the present invention relates to respect to the neutral position of input disk used in explanation; Fig. 6 is that the ideograph of the included live roll of the toroidal continuously variable transmission of the hydraulic pressure control device that mode of execution of the present invention relates to respect to the shift position of input disk used in explanation; Fig. 7 is the figure of the conversion of the ejection capacity in the hydraulic pressure control device that relates to of explanation mode of execution of the present invention; Fig. 8 is the flow chart of conversion control of ejection capacity of the pump-unit of the hydraulic pressure control device that relates to of explanation mode of execution of the present invention; Fig. 9 is the sequential chart of an example of conversion control of ejection capacity of the pump-unit of the hydraulic pressure control device that relates to of explanation mode of execution of the present invention.

In addition, Fig. 4 illustrates the figure of formation as live roll arbitrarily in each live roll of the toroidal continuously variable transmission of stepless speed variator and the input disk that contacts with this live roll.In addition, Fig. 5 and Fig. 6 are the figure from the observed input disk of output disk side, and have only schematically shown an input disk and live roll respectively.

At this; In following illustrated mode of execution; Use the internal-combustion engine (petrol engine, DENG, LPG motor etc.) that produces engine torque to be delivered to the driving source of the driving force of stepless speed variator of the present invention as generation; But the invention is not restricted to this, also can use the motor such as motor that produce motor torque as driving source.In addition, also can use internal-combustion engine and motor as driving source simultaneously.

As shown in Figure 2, as the toroidal continuously variable transmission 1 of the stepless speed variator of having used the pressure medium control gear that this mode of execution relates to be with the corresponding optimum condition of the travelling state of vehicle 1A under from be installed on vehicle 1A, promptly export the torque and so-called CVT (the Continuously Variable Transmission: stepless speed variator) of (continuously) control gear ratio infinitely to driving wheel 27 transmission of drive force as the motor 21 of driving source.This toroidal continuously variable transmission 1 is via being clipped in live roll 4 between input disk 2 and the output disk 3 transmitting torque and through making the vert so-called toroidal continuously variable transmission of change gear ratio of live roll 4 between each input disk 2 and output disk 3.Promptly; This toroidal continuously variable transmission 1 between input disk 2 with ring surface 2a, 3a and output disk 3, clip outer circumferential face for the live roll 4 of ring surface 2a, curved surface that 3a is corresponding, and be utilized in the shearing transmitting torque of the oil film of the traction of formation between these input disk 2, output disk 3 and live rolls 4.Toroidal continuously variable transmission 1 verts through the live roll 4 between the output disk 3 that makes the input disk 2 and the output drive strength that are arranged on the input driving force can infinitely change gear ratio, and this gear ratio is to import the rotational speed ratio of disk 2 and output disk 3.

Particularly, like Fig. 2, Fig. 3, shown in Figure 4, this toroidal continuously variable transmission 1 comprises: as the input disk 2 of the rotary component of input side; Output disk 3 as the rotary component of outlet side; Live roll 4 as transferring elements; Change the gear ratio change portion 5 of unit as gear ratio.Gear ratio change portion 5 has as the gudgeon 6 of bearing unit and moving part 7.In addition, moving part 7 has hydraulic piston portion 8 and as the hydraulic pressure control device 9 of pressure medium control gear.In addition, this toroidal continuously variable transmission 1 comprises electronic control unit (the Electronic Control Unit: electronic control unit) 60 of each one that controls toroidal continuously variable transmission 1.In this toroidal continuously variable transmission 1; Be configured to and import live roll 4 that disk 2 contacts with output disk 3 and move to shift position from the neutral position with respect to input disk 2 and output disk 3 through moving part 7; Thereby change gear ratio, this gear ratio are the rotational speed ratios of input disk 2 and output disk 3.

In addition; The input disk 2 of this mode of execution is equivalent to the rotary component of input side and is equivalent to be used to make clamping pressure to act on the first cramping parts of live roll 4, and output disk 3 is equivalent to the rotary component of outlet side and is equivalent to be used to make clamping pressure to act on the second cramping parts of live roll 4.

For example, from the driving force (torque) of motor 21 sides via be starting mechanism be again that torque-converters 22 or the forward-reverse shifting mechanism 23 etc. of fluid transfer apparatus are transmitted (input) to input disk 2.

The engine torque that motor 21 outputs are used to make the vehicle that this motor 21 is installed to advance or retreat, i.e. driving force.In addition, motor 21 is electrically connected with ECU60, and it drives through this ECU60 control, and the driving force of control output.Driving force from motor 21 is delivered to torque-converters 22 via bent axle 21a.

The driving force that torque-converters 22 transmits from motor 21 to toroidal continuously variable transmission 1 via forward-reverse shifting mechanism 23.Torque-converters 22 comprises pump (pump impeller), turbine (turbine wheel), stator, lock-up clutch.Pump links via the bent axle 21a with motor 21 such as protecgulum, and is set to and can rotates with bent axle 21a and protecgulum.It is relative with said pump that turbine is configured to.This turbine links with input shaft 10 via input shaft 22a, forward-reverse shifting mechanism 23, and to be set to be the center rotation with the axis identical with bent axle 21a with input shaft 10 together.Stator is configured between this pump and the turbine.Lock-up clutch is arranged between this turbine and the protecgulum and with turbine and links.

Therefore, this torque-converters 22 transmits the driving force (engine torque) of motor 21 to pump from bent axle 21a via protecgulum.And, when lock-up clutch is disconnected, to the driving force of this pump transmission via being delivered to turbine, input shaft 22a, input shaft 10 as the working oil of the working fluid between pump and turbine.At this moment, torque-converters 22 can obtain predetermined torque characteristics through stator change flowing of circuit working oil between pump and turbine.And when the lock-up clutch that is attached to turbine engaged with protecgulum, torque-converters 22 made the driving force from motor 21 that is delivered to pump via protecgulum not be directly delivered to input shaft 10 through working oil.Here, through from after the working oil of the hydraulic pressure control device stated 9 supplies carry out the releasing of the joint and the joint of lock-up clutch, the joint that promptly engages, breaks off/disconnections controlled.Hydraulic pressure control device 9 with after the ECU60 that states be connected.Therefore, the joint of lock-up clutch/disconnection control is carried out by ECU60.

Forward-reverse shifting mechanism 23 will be delivered to the input disk 2 of toroidal continuously variable transmission 1 via the driving force from motor 21 that torque-converters 22 transmits.Forward-reverse shifting mechanism 23 is for example by planetary gears, forward gear clutch (friction clutch) and reversing break formations such as (friction brakes), and with the driving force of motor 21 directly or be delivered to input disk 2 after the counter-rotating.Promptly; Via the driving force of the motor 21 of forward-reverse shifting mechanism 23 as to the direction that input disk 2 is rotated in the forward (when vehicle advances; The direction of input disk 2 rotations) effect is rotated in the forward driving force or is passed to input disk 2 as the counterrotating driving force to the direction that makes 2 counterrotatings of input disk (during vehicle rollback, the direction of input disk 2 rotations) effect.Carry out conversion control through the joint of execution forward gear clutch, reversing break and the releasing (that is the joint that, engages, breaks off/disconnection is controlled) of joint based on direction of transfer this forward-reverse shifting mechanism 23, driving force.Through from after the working oil of the hydraulic pressure control device stated 9 supplies carry out conversion control based on direction of transfer forward-reverse shifting mechanism 23, driving force, in other words, joint/disconnections of forward gear clutch, reversing break controlled.Therefore, carry out the conversion control of forward-reverse shifting mechanism 23 through ECU60.

Forward-reverse shifting mechanism 23 for example advances at vehicle and makes the forward gear clutch joint when going and the reversing break is broken off.In addition, when vehicle rollback goes, make the forward gear clutch disconnection and make the reversing brake engages.Thus, the sense of rotation that forward-reverse shifting mechanism 23 can the conversion torque.And forward-reverse shifting mechanism 23 makes forward gear clutch break off when neutral gear and the reversing break is broken off.

Two input disks 2 combine with the input shaft 10 that rotates based on the rotation of motor 21, and are set to can rotate freely through this input shaft 10.Further, each is imported disk 2 and is rotated through the exchanging shaft 11 that produces the rotation identical with input shaft 10.Therefore, each to import disk 2 can be that rotating center is rotated with the spin axis X1 as the input shaft 10 of disk spin axis.This toroidal continuously variable transmission 1 is provided with front side input disk 2 in the front side (motor 21 sides) with respect to exchanging shaft 11 _F, along on the direction of spin axis X1 with respect to front side input disk 2 _FThe rear side (driving wheel 27 sides) of vacating predetermined interval is provided with rear side input disk 2 _R

Front side input disk 2 _FBe supported in exchanging shaft 11 via ball spline 11a.That is front side input disk 2, _FCan be rotated along with the rotation of exchanging shaft 11, and being supported on the exchanging shaft 11 along the mode that moves on the direction of spin axis X1 with respect to this exchanging shaft 11.In other words, front side input disk 2 _FCan not relatively rotate displacement around spin axis X1 with respect to exchanging shaft 11, but can be with respect to exchanging shaft 11 along relatively rotating displacement on the direction of spin axis X1.

On the other hand, rear side input disk 2 _RBe supported in exchanging shaft 11 via the spline embedding part, and through the moving to rear side of the restriction of the loading nut 11b on the rear end that is arranged on exchanging shaft 11 along spin axis X1.Load the rear end screw-thread fit of nut 11b and exchanging shaft 11, and accept from after the pressing force of the oil pressure pressing mechanism 15 stated, the restriction rear side is imported disk 2 _RTo moving of rear side.That is rear side input disk 2, _RBe supported on the exchanging shaft 11, make can be rotated along with the rotation of exchanging shaft 11, its with respect to exchanging shaft 11 to relatively moving of rear side be loaded nut 11b be limited in the precalculated position and can along with exchanging shaft 11 along spin axis X1 mobile to the front side.In other words, rear side input disk 2 _RRelatively do not rotate displacement around spin axis X1 with respect to exchanging shaft 11, and when from after the pressing force of the oil pressure pressing mechanism 15 stated act on when loading on the nut 11b also not with respect to exchanging shaft 11 along displacement relatively on the direction of spin axis X1.In addition, in following explanation, when not needing to distinguish front side input disk 2 especially _FWith rear side input disk 2 _RThe time, simple note is made " input disk 2 ".

Each is imported disk 2 and is formed with opening in central authorities, and has the outstanding gradually shape of center side from the lateral.Each angular surface type of importing the projection of disk 2 becomes the section that makes along spin axis X1 direction and roughly is circular shape, and constitutes the ring surface 2a that respectively imports disk 2.Two input disks 2 are set to make ring surface 2a to face each other.

Output disk 3 will transmit (input) and arrive driving wheel 27 sides to the driving force transmission (output) of each input disk 2, with each input disk 2 output disk will be set respectively accordingly, be provided with two output disks altogether.(motor 21 sides) are provided with front side output disk 3 to this toroidal continuously variable transmission 1 in the front side with respect to exchanging shaft 11 _F, and be provided with rear side output disk 3 at rear side (driving wheel 27 sides) _RFront side output disk 3 _FWith rear side output disk 3 _RAll be arranged on front side input disk 2 with respect to direction along spin axis X1 _FWith rear side input disk 2 _RBetween, furthermore, rear side output disk 3 _RBe arranged on front side output disk 3 _FWith rear side input disk 2 _RBetween.That is, this toroidal continuously variable transmission 1 begins from the front side with front side input disk 2 with respect to the direction along spin axis X1 _F, front side output disk 3 _F, rear side output disk 3 _R, rear side input disk 2 _ROrder be provided with.In addition, in following explanation, when not needing to distinguish front side output disk 3 especially _FWith rear side output disk 3 _RThe time, simple note is made " output disk 3 ".

Each is imported disk 2 and can be provided with coaxially with spin axis X1 with each output disk 3 with rotating freely.Therefore, each output disk 3 can be that rotating center is rotated with spin axis X1.And each output disk 3 is and the roughly the same shape of each input disk 2, that is, each output disk 3 is formed with opening in central authorities, and is the outstanding gradually shape of center side from the lateral.The angular surface type of the projection of each output disk 3 becomes the section that makes along spin axis X1 direction and roughly is circular shape, and constitutes the ring surface 3a of each output disk 3.

And each output disk 3 is arranged between two input disks 2 with respect to the direction along spin axis X1 as stated, and is configured such that each ring surface 3a of each output disk 3 imports the ring surface 2a of disk 2 respectively in the face of each.That is, along in the section of spin axis X1, a front side input disk 2 _F Ring surface 2a and front side output disk 3 _F Ring surface 3a be oppositely arranged and form front side (driving source) cavity C _F, another rear side input disk 2 _R Ring surface 2a and rear side output disk 3 _R Ring surface 3a be oppositely arranged and form another rear side (driven wheel side) cavity C _R

In addition, each output disk 3 is supported on the sleeve cylindraceous that is arranged at the output gear 12 between these two output disks 3 via splined joint portion.That is, but each output disk 3 link together rotatably with output gear 12 one.Output gear 12 by pair of bearings (bearing) 31 (with reference to Fig. 3) but along free rotary ground supporting under the confined state of the displacement of spin axis X1 in midfeather 32 (Fig. 3 with reference to), be set to housing 1a regularly at the inboard midfeather 32 of housing 1a (with reference to Fig. 4).In addition, exchanging shaft 11 inserts among the through hole 12a of the radially inner side in the output gear 12, and output gear 12 is supported to and can rotates relatively with respect to this exchanging shaft 11.Therefore, each output disk 3 is supported to and can rotates relatively with respect to exchanging shaft 11 with output gear 12.

Promptly; In this toroidal continuously variable transmission 1; The position of midfeather 32 is confirmed that by housing 1a the position of bearing 31 is confirmed that by midfeather 32 position of output gear 12 is confirmed by bearing 31; The position of each output disk 3 confirmed by output gear 12, so each output disk 3 is determined with respect to the position of housing 1a.

In addition; Exchanging shaft 11 is along being supported with respect to housing 1a (with reference to Fig. 4) via axial direction central support portion 33 in the central part of the direction of spin axis X1 with the relative rotation, and axial direction central support portion 33 is made up of output gear 12, bearing 31, midfeather 32 etc.That is, this toroidal continuously variable transmission 1 is to comprise the front side cavity C _FAnd rear side cavity C _RBicavate toroidal continuously variable transmission 1, and this toroidal continuously variable transmission 1 is supported to and is provided with front side input disk 2 _F, rear side input disk 2 _R, front side output disk 3 _F, rear side output disk 3 _RExchanging shaft 11 along on the direction of spin axis X1 in this front side cavity C _FWith the rear side cavity C _RBetween can rotate said front side cavity C relatively with respect to housing 1a (with reference to Fig. 4) via axial direction central support portion 33 _FBy front side input disk 2 _FWith front side output disk 3 _FForm said rear side cavity C _RBy rear side input disk 2 _RWith rear side output disk 3 _RForm.

In addition, counter gear 13 and output gear 12 engagements, output shaft 14 links with this counter gear 13.Therefore, output gear 12 is along with the rotation of each output disk 3 is rotated, and is rotated with the counter gear 13 of these output gear 12 engagements, thereby output shaft 14 is rotated.And this output shaft 14 is connected with driving wheel 27 via power transmission mechanism 24, differential gear 25 etc., and driving force is transmitted (output) to driving wheel 27 via power transmission mechanism 24, differential gear 25 etc.

Power transmission mechanism 24 carries out the transmission of driving force between toroidal continuously variable transmission 1 and differential gear 25.Power transmission mechanism 24 is configured between output disk 3 and the differential gear 25.Differential gear 25 carries out the transmission of driving force between power transmission mechanism 24 and driving wheel 27.Differential gear 25 is configured between power transmission mechanism 24 and the driving wheel 27.Transmission shaft 26 links with differential gear 25.Driving wheel 27 is installed on the transmission shaft 26.

Live roll 4 is arranged between input disk 2 and the output disk 3 with the mode that contacts with input disk 2 and output disk 3, and transmits from the driving force of importing disk 2 to output disk 3.That is, the outer circumferential face of live roll 4 forms and ring surface 2a, the corresponding curved surface of contact 4a of 3a.And; Live roll 4 is sandwiched between input disk 2 and the output disk 3; Thereby surface of contact 4a can contact with

ring surface

2a, 3a; The surface of contact 4a of each live roll 4 respectively through after the gudgeon 6 stated contact with

ring surface

2a, 3a, to be supported to the spin axis X2 as the live roll spin axis be that rotating center can rotate freely to each live roll 4 simultaneously.Live roll 4 uses the shearing of the oil film that between the surface of contact 4a of

ring surface

2a, 3a and the live roll 4 of input disk 2 and output disk 3, forms through the traction that is supplied to toroidal continuously variable transmission 1 to come transmission of drive force (torque).

For two live rolls 4 being set respectively, four live rolls are set altogether by a pair of input disk 2 and the cavity that output disk 3 forms.That is, this toroidal continuously variable transmission 1 has for the front side cavity C _FBe set to a pair of two live rolls 4 and for the rear side cavity C _RBe set to two a pair of live rolls 4.For each front side cavity C _F, the rear side cavity C _RBeing set to a pair of live roll 4 is oppositely arranged across spin axis X1 each other.

More particularly, live roll 4 comprises live roll body 41 and foreign steamer 42.Live roll body 41 is formed with the above-mentioned surface of contact 4a that contacts with input disk 2, the ring surface 2a of

output disk

3,3a on outer circumferential face.Live roll body 41 via bearing portion (radial bearing) but 43a by free rotary ground supporting in the running shaft 42a of foreign steamer 42.In addition, live roll body 41 via bearing portion (thrust-bearing) but 43b by free rotary ground supporting on the face relative of foreign steamer 42 with live roll body 41.Therefore, live roll body 41 can be that rotating center is rotated with the spin axis X2 of running shaft 42a.

Above-mentioned running shaft 42a and eccentric shaft 42b are formed on the foreign steamer 42 together.Eccentric shaft 42b forms and makes spin axis X2 ' be positioned at the position with respect to the spin axis X2 skew of running shaft 42a.Eccentric shaft 42b via bearing portion (radial bearing) but the 43c free rotary ground supporting in embedding part 6d, embedding part 6d after form recess among the roller support 6a of the gudgeon 6 stated.Therefore, foreign steamer 42 can be that the center is rotated with the spin axis X2 ' of eccentric shaft 42b.That is, live roll 4 can be that the center is rotated with spin axis X2 and spin axis X2 ' with respect to gudgeon 6, that is, can be to revolve round the sun and can be that rotation is carried out at the center with spin axis X2 in the center with spin axis X2 '.Thus, live roll 4 has and can therefore for example can allow the inequality of part distortion or parts precision along the formation that moves on the direction of spin axis X1.

At this, input shaft 10 is pushed (end load) mechanism 15 with the oil pressure of pressing the change unit as surface of contact and is connected.

Oil pressure pressing mechanism 15 is that input disk 2 is contacted with live roll 4 with output disk 3, and is used for clamping between as the input disk 2 of these first cramping parts and the output disk 3 as the second cramping parts cramping unit of the clamping pressure of live roll 4.The clamping pressure that oil pressure pressing mechanism 15 is used to clamp this live roll 4 through change changes the surface of contact pressure of contact segment of the surface of contact 4a of the

ring surface

2a, 3a and the live roll 4 that act on input disk 2, output disk 3.This oil pressure pressing mechanism 15 is that the oil pressure of working oil acts between input disk 2 and the output disk 3 and clamps the clamping pressure of live roll 4 and regulate this clamping pressure through the pressure as the working oil of working medium; Regulate the surface of contact of

ring surface

2a, 3a and surface of contact 4a thus and press, the clamping pressure that said working oil is supplied to as surface of contact pressure-controlled pressure chamber produces the 15a of hydraulic chamber.

This oil pressure pressing mechanism 15 has clamping pressure and produces 15a of hydraulic chamber and cramping pressing force piston 15b.Oil pressure pressing mechanism 15 is imported disk cramping pressing force acting surface 29 through front side input disk cramping pressing force acting surface 28 and rear side that the oil pressure that will be supplied to this clamping pressure to produce the working oil of the 15a of hydraulic chamber acts on the pressure acting surface that is rotated as the rotation along with input disk 2, can act on live roll 4 is clipped in the clamping pressure between input disk 2 and the output disk 3.

Particularly, clamping pressure produces the 15a of hydraulic chamber and is set at a side of importing disks 2 along the direction of spin axis X1 with respect to two.At this, clamping pressure produces the 15a of hydraulic chamber and is set at front side input disk 2 with respect to the direction along spin axis X1 _FSide, and be configured in input shaft 10 and front side input disk 2 _FBetween.According to running state, working oil is supplied to the inside that clamping pressure produces the 15a of hydraulic chamber from hydraulic pressure control device 9.

Cramping pressing force piston 15b forms discoideus, and an end that is set at exchanging shaft 11 makes its center and spin axis X1 unanimous on the whole.Cramping pressing force piston 15b be set at exchanging shaft 11 be provided with rear side input disk 2 _RThe end of end opposition side, i.e. front side (motor 21 sides).Cramping pressing force piston 15b is with respect to direction and front side input disk 2 along spin axis X1 _FBe configured in to devices spaced apart input shaft 10 and front side input disk 2 _FBetween.Above-mentioned clamping pressure produces the 15a of hydraulic chamber and is set at this cramping pressing force piston 15b and front side input disk 2 _FBetween.

In addition, cramping pressing force piston 15b can be center rotation with this exchanging shaft 11 with spin axis X1 with respect to exchanging shaft 11, and be set to can be along moving on the direction of spin axis X1.That is, cramping pressing force piston 15b is supported on the exchanging shaft 11, can be rotated along with the rotation of exchanging shaft 11, and can be along with exchanging shaft 11 mobile along the direction of spin axis X1.Furthermore, cramping pressing force piston 15b does not relatively rotate displacement with respect to exchanging shaft 11 around spin axis X1, not along relatively moving on the direction of spin axis X1 yet.Therefore, rear side input disk 2 _R, exchanging shaft 11 and cramping pressing force piston 15b can be being that the center rotates integratedly around spin axis X1, and can be along moving on the direction of spin axis X1.In addition, front side input disk 2 _FCan import disk 2 with rear side _R, exchanging shaft 11 and cramping pressing force piston 15b be that the center rotates integratedly with spin axis X1 together, on the other hand, can also be through ball spline 11a with respect to this rear side input disk 2 _R, exchanging shaft 11 and cramping pressing force piston 15b be along relatively moving on the direction of spin axis X1.

In addition, cramping pressing force piston 15b also links with input shaft 10, and can be the center rotation with spin axis X1 with this input shaft 10, and also be set to can be along relatively moving on the direction of spin axis X1.Particularly, cramping pressing force piston 15b and exchanging shaft 11 form, and cramping pressing force piston 15b and exchanging shaft 11 link with mode and input shaft 10 that can transmission of drive force via the 11c of splined joint portion.Cramping pressing force piston 15b, exchanging shaft 11 link via 11c of splined joint portion and input shaft 10, and spline that the 11c of splined joint portion is formed by the spin axis X1 in the outer circumferential face upper edge of cylindrical part 11d and the spline that spin axis X1 forms in the inner peripheral surface upper edge of input shaft 10 carry out splined joint and form.At this, cylindrical part 11d is the outstanding forward part that is provided with on the face of the front side of cramping pressing force piston 15b, and is so that its central axis and spin axis X1 mode unanimous on the whole form part cylindraceous.

That is rear side input disk 2, _R, exchanging shaft 11 and cramping pressing force piston 15b can become one and be the center rotation with spin axis X1 via this 11c of splined joint portion and input shaft 10; On the other hand, can be with respect to this input shaft 10 along relatively moving on the direction of spin axis X1.Driving force from input shaft 10 is delivered to exchanging shaft 11 via the 11c of this splined joint portion, cramping pressing force piston 15b, and is delivered to front side input disk 2 from exchanging shaft 11 _F, rear side input disk 2 _R

In addition, front side input disk 2 _FHave above-mentioned front side input disk cramping pressing force acting surface 28, on the other hand, cramping pressing force piston 15b has above-mentioned rear side input disk cramping pressing force acting surface 29.Front side input disk cramping pressing force acting surface 28 is arranged on front side input disk 2 _FIn back side surface of contact, ring surface 2a that contacts with live roll 4 of conduct on.Rear side input disk cramping pressing force acting surface 29 be arranged among the cramping pressing force piston 15b along on the face relative on the direction of spin axis X1 with front side input disk cramping pressing force acting surface 28.It is relative with front side input disk cramping pressing force acting surface 28 that rear side input disk cramping pressing force acting surface 29 is set to produce the 15a of hydraulic chamber across above-mentioned clamping pressure.At cramping pressing force piston 15b and front side input disk 2 _FBetween, clamping pressure produces the 15a of hydraulic chamber and is imported disk cramping pressing force acting surface 29 with respect to the direction description along spin axis X1 by front side input disk cramping pressing force acting surface 28 with rear side.Promptly; Import in the disk cramping pressing force acting surface 29 with rear side at front side input disk cramping pressing force acting surface 28; Front side input disk cramping pressing force acting surface 28 is relative with the clamping pressure generation 15a of hydraulic chamber at rear side, and rear side input disk cramping pressing force acting surface 29 is relative with the clamping pressure generation 15a of hydraulic chamber in the front side.

Therefore; Oil pressure pressing mechanism 15 makes the cramping pressing force act on front side input disk cramping pressing force acting surface 28 and rear side input disk cramping pressing force acting surface 29 through the oil pressure of the working oil of in clamping pressure produces the 15a of hydraulic chamber, supplying, thereby makes front side input disk 2 _FTowards from oil pressure pressing mechanism 15 side direction rear sides away from direction move, and make rear side input disk 2 _RWith exchanging shaft 11 towards moving to the near direction of oil pressure pressing mechanism 15 side joints from rear side.That is front side input disk 2, _FWith respect to exchanging shaft 11 along relatively moving on the direction of spin axis X1.Then, oil pressure pressing mechanism 15 is through making front side input disk 2 _FMove and make rear side input disk 2 from oil pressure pressing mechanism 15 side direction rear sides _RMove to direction with exchanging shaft 11, thereby make front side input disk 2 near the front side _FTo front side output disk 3 _FSide joint is near and make rear side import disk 2 _RTo rear side output disk 3 _RSide joint is near, and imports disk 2 in the front side _FWith front side output disk 3 _FBetween and rear side input disk 2 _RWith rear side output disk 3 _RBetween produce clamping pressure.At this moment, the counter-force portion of bearing of the cramping pressing force that is produced as oil pressure pressing mechanism 15 with the loading nut 11b of the rear end screw-thread fit of exchanging shaft 11 works, that is, bear the cramping pressing force and limit rear side input disk 2 _RWith respect to exchanging shaft 11 moving to rear side.Thus, oil pressure pressing mechanism 15 is imported disk 2 in the front side _FWith front side output disk 3 _FBetween and rear side input disk 2 _RWith rear side output disk 3 _RBetween produce clamping pressure, therefore can each live roll 4 be clipped in front side input disk 2 respectively through predetermined clamping pressure _FWith front side output disk 3 _FBetween and rear side input disk 2 _RWith rear side output disk 3 _RBetween.Consequently, can prevent to import skidding between disk 2, output disk 3 and the live roll 4, and can keep suitable traction state.

At this; Through after 9 controls of the hydraulic pressure control device stated produce the amount or the oil pressure of the working oil of the 15a of hydraulic chamber supply to clamping pressure; Thereby will be based on the cramping pressing force of oil pressure pressing mechanism 15, in other words, clamping pressure is controlled to be based on the predetermined size to the input torque of toroidal continuously variable transmission 1.Promptly; Produce the amount or the oil pressure of the working oil of the 15a of hydraulic chamber supply through hydraulic pressure control device 9 control to clamping pressure, surface of contact on the contact segment between the surface of contact 4a of ring surface 2a, 3a and live roll 4 of input disk 2, output disk 3 is voltage-controlled to be made as based on the predetermined size to the input torque of toroidal continuously variable transmission 1 thereby will act on.In other words, in toroidal continuously variable transmission 1, can press according to the surface of contact of ring surface 2a, 3a and surface of contact 4a and control the transmitting torque (torque capacity) that can between input disk 2, output disk 3 and live roll 4, transmit.Hydraulic pressure control device 9 with after the ECU60 that states be connected.Therefore, through the size of ECU60 control based on the cramping pressing force of oil pressure pressing mechanism 15, the in other words size of surface of contact pressure.

Gear ratio change portion 5 is that oil pressure changes gear ratio through being supplied to the pressure as the working oil of the speed Control hydraulic chamber 82 of speed Control pressure chamber.Gear ratio change portion 5 has gudgeon 6 and moving part 7 as stated, and live roll 4 is moved with respect to the spin axis X1 of input disk 2 and output disk 3 with gudgeon 6 and live roll 4 is verted with respect to this input disk 2 and output disk 3 through moving part 7 and change gear ratio.Furthermore; The oil pressure of the working oil of gear ratio change portion 5 through being supplied to speed Control hydraulic chamber 82 makes the speed Control pressing force act on the gudgeon 6 of supporting live roll 4; Make live roll 4 move to shift position and this live roll 4 is verted from neutral position, thereby change gear ratio with respect to input disk 2 and output disk 3 with this gudgeon 6.

At this; Gear ratio is meant the rotational speed ratio of input disk 2 and output disk 3; In other words; The rotation rotating ratio usually, can be expressed as " gear ratio=outlet side contact radius (contact radius that live roll 4 contacts with output disk 3 (point of contact with spin axis X1 distance))/input side contact radius (importing the contact radius that disk 2 contacts with live roll 4) ".

Particularly, each gudgeon 6 is swivel bearing live roll 4 freely respectively, and supports this live roll 4 and make it move with output disk 3 and can freely vert with output disk 3 with respect to input disk 2 with respect to input disk 2.Gudgeon 6 has roller support 6a and as the running shaft 6b of axial region.

Roller support 6a is formed with space portion 6c, and live roll 4 is configured among the space portion 6c, and is formed with the embedding part 6d of concavity among this space portion 6c.And gudgeon 6 is inserted among the embedding part 6d through the eccentric shaft 42b of live roll 4 as stated, thereby in its space portion 6c, can freely support live roll 4 rotatably.In addition, roller support 6a is set to and can moves integratedly with running shaft 6b.Running shaft 6b forms from the shoulder 6e of roller support 6a outstanding.

At this, the shoulder 6e of roller support 6a is set in roller support 6a, erect the wall portion that is provided with respect to the wall portion that is provided with embedding part 6d.Shoulder 6e is set to a pair of in roller support 6a with respect to the wall portion that is provided with embedding part 6d, this a pair of shoulder 6e is set to face each other.And each other in the face of being provided with, roller support 6a forms above-mentioned space portion 6c through this a pair of shoulder 6e.At this, in roller support 6a, the wall portion and a pair of shoulder 6e that are provided with embedding part 6d form.

And running shaft 6b forms outstanding from a pair of shoulder 6e of roller support 6a respectively as stated.Each running shaft 6b forms column, and to be set to be the rotating center rotation with mutual coaxial spin axis X3.Gudgeon 6 via after state lower link 16a, go up connecting rod 17a, cylinder body 86 etc. and be supported on the housing 1a, make that roller support 6a is that rotating center rotates freely with this running shaft 6b with spin axis X3.In addition; Gudgeon 6 is supported on the housing 1a via lower link 16a, last connecting rod 17a, cylinder body 86 etc.; Make roller support 6a with this running shaft 6b along freely moving on the direction of spin axis X3, and be constituted as through after the moving part 7 stated can be along moving on the direction of spin axis X3.

In addition, facing this lower link 16a and last connecting rod 17a down at length explains.

To two gudgeons 6 respectively being set, 6, four gudgeons 6 of four gudgeons are set altogether support four live rolls 4 respectively by a pair of input disk 2 and the cavity that output disk 3 forms.That is, in this toroidal continuously variable transmission 1, to the front side cavity C _FBe provided with a pair of two gudgeons 6 that support two live rolls 4 respectively, and to the rear side cavity C _RBe provided with a pair of two gudgeons 6 that support two live rolls 4 respectively.

At this, gudgeon 6 supporting live rolls 4 make the spin axis X2 of live roll 4 be parallel to the plane vertical with the spin axis X3 of running shaft 6b.In addition, gudgeon 6 is configured to make the spin axis X3 of running shaft 6b to be parallel to and input disk 2 plane vertical with the spin axis X1 of output disk 3.That is, gudgeon 6 can make live roll 4 move along spin axis X3 with respect to the spin axis X1 of input disk 2 and output disk 3 through in the plane vertical with spin axis X1, moving along spin axis X3.In addition, gudgeon 6 is through being that rotating center is rotated with spin axis X3, and can make live roll 4 is freely to vert with output disk 3 with respect to input disk 2 in the center with this spin axis X3 in the plane vertical with spin axis X3.In other words, gudgeon 6 through after the power of verting stated be applied in live roll 4 so that its mode that can vert supports live roll 4.

Moving part 7 make live roll 4 with gudgeon 6 along moving on the direction of spin axis X3, and have hydraulic piston portion 8 and hydraulic pressure control device 9 as stated.

Hydraulic piston portion 8 is constituted as and comprises as speed Control piston of piston 81 and speed Control hydraulic chamber 82, and the oil pressure that bears the working oil that imports to speed Control hydraulic chamber 82 of the lip part 84 through speed Control piston 81 makes gudgeon 6 move going up along the both direction (A1 direction and A2 direction) of spin axis X3.That is, hydraulic piston portion 8 makes the speed Control pressing force act on the lip part 84 on the gudgeon 6 through the oil pressure to the working oil of speed Control hydraulic chamber 82 supply.

Particularly, speed Control piston 81 comprises piston base 83 and lip part 84.Piston base 83 forms cylindric, and insert the end of running shaft 6b, and is fixed on the piston base 83 with respect to spin axis X3 direction and around the direction of spin axis X3.

Lip part 84 by be set to regularly from piston base 83 to piston base 83 radially, in other words, running shaft 6b's is radially outstanding, and can be with the running shaft 6b of piston base 83 and gudgeon 6 along moving on the direction of spin axis X3.It is tabular that the spin axis X3 that lip part 84 centers on running shaft 6b forms annulus.

Speed Control hydraulic chamber 82 forms parts 85 by hydraulic chamber and forms.This hydraulic chamber form parts 85 comprise as first form parts cylinder body 86 and as second form parts lower cover 87.That is, hydraulic chamber forms the wall that parts 85 constitute speed Control hydraulic chamber 82, and with respect to along the movement direction (stroke directions) of gudgeon 6, be that the direction of spin axis X3 is divided into cylinder body 86 and lower cover 87.Cylinder body 86 is formed with the recess of the space portion that constitutes speed Control hydraulic chamber 82.For the opening of the recess that stops up cylinder body 86, lower cover 87 is fixed to this cylinder body 86, and thus, it is cylindric (tubular) at center that speed Control hydraulic chamber 82 is divided into spin axis X3 by cylinder body 86 and lower cover 87.This cylinder body 86 and lower cover 87 are fixed on cylinder body 86 and housing 1a lower cover 87 side opposition sides.In addition, between cylinder body 86 and lower cover 87, be provided with the working oil that prevents in the speed Control hydraulic chamber 82 packing ring 88 to external leaks.

And lip part 84 is contained in working oil and is imported in the speed Control hydraulic chamber 82 wherein, and along on the direction of spin axis X3 this speed Control hydraulic chamber 82 being separated into two hydraulic chamber, that is, and first OP1 of hydraulic chamber and second OP2 of hydraulic chamber.First OP1 of hydraulic chamber through the oil pressure that is supplied to inner working oil make gudgeon 6 with lip part 84 along moving on the first direction A1 of spin axis X3; On the other hand, second OP2 of hydraulic chamber makes gudgeon 6 move along the reciprocal second direction A2 as first direction with lip part 84 through the oil pressure that is supplied to inner working oil.

The tip portion of the radial outside of lip part 84 is provided with the sealed member S1 of annular; Therefore; First OP1 of hydraulic chamber of the speed Control hydraulic chamber 82 that this lip part 84 is separated and second OP2 of hydraulic chamber by sealing parts S1 sealing, make working oil can not leak each other respectively.On the peripheral part of piston base 83; And form between the cylinder body 86 and lower cover 87 of parts 85 as the hydraulic chamber that forms speed Control hydraulic chamber 82; Be provided with sealed member S2, S3, the S4 of ring-type; Therefore, sealed by these sealed members S2, S3, S4 between the peripheral part of piston base 83 and cylinder body 86, the lower cover 87, thereby the working oil in the speed Control hydraulic chamber 82 can be to external leaks.

In addition, because a pair of input disk 2 respectively is provided with two live rolls 4, gudgeon 6 with output disk 3, therefore a pair of input disk 2 respectively is provided with two first OP1 of hydraulic chamber and second OP2 of hydraulic chamber with output disk 3.At this, in this a pair of gudgeon 6, the position of first OP1 of hydraulic chamber and second OP2 of hydraulic chamber relation is exchanged with respect to each gudgeon 6.That is, become second OP2 of hydraulic chamber of another gudgeon 6, become first OP1 of hydraulic chamber of another gudgeon 6 as the hydraulic chamber of second OP2 of hydraulic chamber of a gudgeon 6 as the hydraulic chamber of first OP1 of hydraulic chamber of a gudgeon 6.Therefore, in toroidal continuously variable transmission shown in Figure 21, oppositely mobile each other through the oil pressure in first OP1 of hydraulic chamber or second OP2 of hydraulic chamber along spin axis X3 for two live rolls 4 of a pair of input disk 2 and output disk 3 settings.

Hydraulic pressure control device 9 is to producing the various piece supply working oil of the 15a of hydraulic chamber, torque-converters 22, forward-reverse shifting mechanism 23 iso-variable velocity devices such as the speed Control hydraulic chamber 82 of hydraulic piston portion 8, the clamping pressure of oil pressure pressing mechanism 15.At this, hydraulic pressure control device 9 is controlled amount or the oil pressure that produces the working oil of the 15a of hydraulic chamber, 82 supplies of speed Control hydraulic chamber to clamping pressure at least.

Hydraulic pressure control device 9 through as after the pump-unit 92 (with reference to Fig. 1) of the pump unit stated suck, during pressurization, ejection are stored in food tray 91 (Fig. 1 with reference to) and to the working oil of the various piece supply of speed changer.At this, pump-unit 92 for example drives with rotation as the bent axle 21a of the output shaft of the motor 21 that produces driving force linkedly, and suck, pressurization, ejection be stored in the working oil in the food tray 91.

The working oil that hydraulic pressure control device 9 is pressurizeed by pump-unit 92 to supplies such as various flow control valves via pressure regulator valve.Various flow control valves are constituted as and comprise valve core of the spool valve, o etc., and comprise: the flow control valve that Control work oil is discharged from first OP1 of hydraulic chamber, second OP2 of hydraulic chamber to supply or the working oil of first OP1 of hydraulic chamber, second OP2 of hydraulic chamber; The flow control valve that Control work oil is discharged from supply from the clamping pressure generation 15a of hydraulic chamber to the clamping pressure generation 15a of hydraulic chamber or working oil etc.The flow control valve of hydraulic pressure control device 9; For example; Through make the position displacement of valve core of the spool valve based on the o that driving current drove, control the flow or the oil pressure that produce the 15a of hydraulic chamber supply and produce the working oil that the 15a of hydraulic chamber discharges from first OP1 of hydraulic chamber, second OP2 of hydraulic chamber, clamping pressure to first OP1 of hydraulic chamber, second OP2 of hydraulic chamber, clamping pressure from the control command value input of ECU60 input.In addition; When the oil pressure in the downstream side of pressure regulator valve during more than or equal to predetermined oil pressure; That is, when pressing, pressure is adjusted to predetermined pipeline pressure thereby pressure regulator valve makes the working oil that is positioned at downstream side return food tray 91 more than or equal to the pipeline of the initial pressure that is used as hydraulic pressure control device 9.

In addition, at length explain in the face of this hydraulic pressure control device 9 down.

For example; If ECU60 controls the flow control valve of hydraulic pressure control device 9 and the working oil that pump-unit 92 is pressurizeed is discharged to first OP1 of hydraulic chamber supply and with the working oil in second OP2 of hydraulic chamber, then the oil pressure of first OP1 of hydraulic chamber acts on lip part 84 and becomes " oil pressure of the oil pressure of first OP1 of hydraulic chamber＞second OP2 of hydraulic chamber ".Thus, the lip part of hydraulic piston portion 8 84 is pushed towards the first direction A1 along spin axis X3, and live roll 4 with gudgeon 6 along moving on the first direction A1 of spin axis X3.Likewise; If ECU60 controls the flow control valve of hydraulic pressure control device 9 and the working oil that pump-unit 92 is pressurizeed is discharged from first OP1 of hydraulic chamber and in second OP2 of hydraulic chamber, supplied, then the oil pressure of second OP2 of hydraulic chamber acts on lip part 84 and becomes " oil pressure of the oil pressure of first OP1 of hydraulic chamber＜second OP2 of hydraulic chamber ".Thus, the lip part of hydraulic piston portion 8 84 is pushed towards the second direction A2 along spin axis X3, and live roll 4 with gudgeon 6 along moving on the second direction A2 of spin axis X3.At this moment, according to the amount of movement of the valve core of the spool valve of flow control valve, regulate live roll 4 moving to first direction A1 or second direction A2.

Therefore; This moving part 7 drives hydraulic pressure control device 9 through ECU60 and controls the oil pressure in each speed Control hydraulic chamber 82 of hydraulic piston portion 8; Can be to the predetermined speed Control pressing force of the lip part of speed Control piston 81 84 effects, and can make live roll 4 with gudgeon 6 along the second direction of spin axis X3, be to move on first direction A1 and the second direction A2.At this moment, as stated, a pair of gudgeon 6 and a pair of live roll 4 that are provided with for a pair of input disk 2 and output disk 3 oppositely move along spin axis X3 each other.And; Gear ratio change portion 5 makes a pair of live roll 4 vert with output disk 3 with respect to importing disk 2 to move each other with the corresponding shift position of gear ratio (with reference to Fig. 6) and make this live roll 4 from the neutral position (with reference to Fig. 5) with respect to input disk 2 and output disk 3 with a pair of gudgeon 6 in the other direction through this moving part 7, can change gear ratio.

At this, as shown in Figure 5, live roll 4 is positions that gear ratio is fixed with respect to the neutral position of input disk 2 and output disk 3, and is to make the power of verting that live roll 4 verts with respect to input disk 2 and output disk 3 can not act on the position of this live roll 4.That is, be positioned under the fixing state of neutral position and gear ratio at live roll 4, the spin axis X2 of live roll 4 is set in the plane that comprises spin axis X1 and the plane vertical with spin axis X3.In other words, on the neutral position of live roll 4 (gear ratio fixedly time), live roll 4 is set at this live roll 4 along the position of the direction of spin axis X3 spin axis X2 passes the position of (quadrature) spin axis X1.At this moment, in the point of contact of live roll 4 and input disk 2, output disk 3, the sense of rotation of live roll 4 (sense of rotation) is consistent with the sense of rotation of importing disk 2, output disk 3; Consequently; The power of verting does not act on the live roll 4, and therefore, live roll 4 is staying in this neutral position; Continue rotation with input disk 2 simultaneously, the gear ratio during this immobilizes.

Because basically only have driving force (torque) from the power that acts on the live roll 4 of input disk 2 this moment, so the hydraulic piston portion 8 of moving part 7 and hydraulic pressure control device 9 only will be used for gudgeon 6 through the masterpiece that oil pressure is resisted this driving force.Promptly; When the gudgeon 6 of live roll 4 and supporting live roll 4 is positioned at the neutral position; As stated; The speed Control pressing force F2 (with reference to Fig. 5) of the size through making the tangential force F1 (with reference to Fig. 5) of resistant function on the point of contact of input disk 2, output disk 3 and live roll 4 according to input torque acts on lip part 84; And make the tangential force F1 and the speed Control pressing force F2 balance that act on the live roll 4, thus with live roll 4 and the fixed-site of gudgeon 6 that supports this live roll in the neutral position and gear ratio is fixed.

On the other hand, as shown in Figure 6, the shift position of live roll 4 is positions that gear ratio changes, and is to make live roll 4 be used for the position on this live roll 4 with respect to input disk 2 and the masterpiece that verts that output disk 3 verts.Promptly; Be positioned under the state that shift position and gear ratio change at live roll 4, the spin axis X2 of live roll 4 is set in plane that comprises spin axis X1 and the plane vertical with spin axis X3 the position after moving along the first direction A1 of spin axis X3 or second direction A2.In other words, in the shift position (during speed change) of live roll 4, the position along the direction of spin axis X3 of live roll 4 is set at the position of passing spin axis X1 from the spin axis X2 of this live roll 4, i.e. position after the neutral position skew.At this moment, in the point of contact of live roll 4 and input disk 2, output disk 3, the sense of rotation of live roll 4 is inconsistent with the sense of rotation of input disk 2, output disk 3, and thus, the masterpiece that verts is used for live roll 4.Consequently; The power of verting that acts on live roll 4 makes breaks away between live roll 4 and input disk 2 and output disk 3; Live roll 4 verts with output disk 3 with respect to input disk 2; And live roll 4 changes with the input side contact radius of input disk 2 and the outlet side contact radius of live roll 4 and output disk 3, and therefore, gear ratio changes.

For example; Shown in Figure 6 like this; In the state that input disk 2 rotates along the arrow B direction (counterclockwise) among Fig. 6; Live roll 4 is towards along the second direction A2 of spin axis X3 (with the opposite direction of movement direction of input disk 2 on the point of contact of live roll 4 and input disk 2, that is, the direction opposite with the sense of rotation of input disk 2 (along the direction of the sense of rotation of output disk 3)) skew.So; In the point of contact of live roll 4 and input disk 2; The masterpiece of circumferencial direction of input disk 2 is used for live roll 4, and makes the masterpiece that verts of the direction (live roll 4 is away from the direction of the spin axis X1 of input disk 2) that live roll 4 moves to the perimeter sides of input disk 2 be used for live roll 4.Consequently; Live roll 4 verts; Make the point of contact of live roll 4 and input disk 2 move and the point of contact of live roll 4 and output disk 3 moves to the radially inner side of output disk 3, and gear ratio changes to reducing side, and upgrade to the radial outside of input disk 2.Then, live roll 4 is got back to the neutral position once more, thereby the gear ratio after the change is immobilized.

Otherwise; When lowering category; Live roll 4 is towards first direction A1 (movement direction of the input disk 2 on the point of contact of live roll 4 and input disk 2, that is, the direction (direction opposite with the sense of rotation of output disk 3) of the sense of rotation of disk 2 is imported on the edge) skew along spin axis X3.So; In the point of contact of live roll 4 and input disk 2; The masterpiece of circumferencial direction of input disk 2 is used for live roll 4, and makes the masterpiece that verts of the direction (making the directions of live roll 4 near the spin axis X1 of input disks 2) that live roll 4 moves to the central side of input disk 2 be used for live roll 4.Consequently; Live roll 4 verts; Make the point of contact of live roll 4 and input disk 2 move and the point of contact of live roll 4 and output disk 3 moves to the radial outside of output disk 3, and gear ratio changes to increasing side, and lower category to the radially inner side of input disk 2.Then, live roll 4 returns the neutral position once more, thereby the gear ratio after the change is immobilized.

At this, the position of this live roll 4 is by path increment and with respect to the tilt angle decision of importing disk 2 and output disk 3.The path increment of live roll 4 be the neutral position that the spin axis X2 with live roll 4 is passed the spin axis X1 of input disk 2 and output disk 3 be the reference position, from this neutral position to the amount of movement of first direction A1 or second direction A2 as path increment; Furthermore, be and based on the corresponding amount of the path increment (side-play amount) of neutral position.The tilt angle of live roll 4 is that to be orthogonal to position as the spin axis X1 of the rotating center of input disk 2 and output disk 3 with the spin axis X2 as the rotating center of live roll 4 be the reference position, begins the angle of inclination (angle of inclination of acute side) with respect to input disk 2 and output disk 3 from this reference position; In other words, be the angle of swing that centers on spin axis X3.And the gear ratio of this toroidal continuously variable transmission 1 is by the tilt angle decision of live roll 4 with respect to input disk 2 and output disk 3, and this tilt angle is by the integral value decision based on the path increment (side-play amount) of the neutral position of live roll 4.

In addition, this toroidal continuously variable transmission 1 comprises that lower link mechanism 16 and last linkage mechanism 17 are as being used to make a pair of live roll 4 and the reciprocal mobile synchronous mechanism of gudgeon 6 along spin axis X3 that is provided with for a pair of input disk 2 and output disk 3.

Lower link mechanism 16 has the lower link 16a as linkage component, and on the other hand, last linkage mechanism 17 has the last connecting rod 17a as linkage component.Lower link 16a links a pair of gudgeon 6 in the tip side that is provided with speed Control piston 81 (between the shoulder 6e of cylinder body 86 and roller support 6a) of the running shaft 6b of gudgeon 6 via the 6f of bearing portion (radial bearing) of spherical bearing.Last connecting rod 17a links a pair of gudgeon 6 in the other end side (another shoulder 6e side of roller support 6a) of the running shaft 6b of gudgeon 6 via the 6f of bearing portion (radial bearing) as spherical bearing.

And, lower link 16a, go up connecting rod 17a be bearing in respectively via cylinder body 86 be fixed to the lower supporting rod 16b of housing 1a lower support axle 16c, be fixed on the upper support axle 17c of upper supporting column 17b of housing 1a.Lower support axle 16c, upper support axle 17c all form cylindric, and are in the direction parallel with spin axis X1 and they can not relatively move with respect to housing 1a by the central axis that is arranged so that them regularly.And; Lower link 16a, going up connecting rod 17a and be constituted as through respectively by this lower support axle 16c, upper support axle 17c supporting, can be fulcrum with this lower support axle 16c, upper support axle 17c, promptly the central axis of following supporting axle 16c, upper support axle 17c is that axis of oscillation X4 swings as seesaw.

Therefore; Lower link mechanism 16, go up linkage mechanism 17 through lower link 16a, go up connecting rod 17a around the central axis of lower support axle 16c, upper support axle 17c, be that axis of oscillation X4 swings, can make a pair of gudgeon 6 towards moving synchronously along the reciprocal of spin axis X3.In addition, nozzle 17d is installed on the upper supporting column 17b, this nozzle 17d is provided with spray-hole 17e, and working oil sprays as above-mentioned traction from this spray-hole 17e.

In addition, as the synchronous mechanism of rotation that impels a plurality of gudgeons 6 around spin axis X3, toroidal continuously variable transmission 1 comprises lazy-tongs 18.Lazy-tongs 18 have synchronous hawser 19 and a plurality of fixed pulley 20.The frictional force of lazy-tongs 18 through the fixed pulley on the running shaft 6b that is arranged on each gudgeon 6 regularly 20 and hawser 19 synchronously is delivered to another gudgeon 6 with the rotating torques of a gudgeon 6; Can impel a plurality of gudgeons 6 is that the rotation of rotating center is synchronous with spin axis X3, and hawser 19 reversally is erected between the adjacent fixed pulley 20 with the mode of intersecting once on spin axis X1 direction or spin axis X2 direction synchronously.

Consequently; In the action (gear shifting operation) of verting of each live roll 4, each gudgeon 6; Even because of not acting under the situation of a plurality of live rolls 4 equably as the parts precision of the gudgeon 6 of the supporting construction of a plurality of live rolls 4 or the unequal clamping pressure of oil pressure pressing mechanism 15 that causes of assembly precision; Perhaps wait under the situation that causes speed change responsiveness generation little deviation the poor of oil circuit resistance because of hydraulic pressure control device 9; These lazy-tongs 18 also can make the mutual synchronizing linkedly of the rotation of a plurality of gudgeons 6 and can make the mutual synchronizing of action of verting of a plurality of live rolls 4, therefore can improve the speed Control precision of toroidal continuously variable transmission 1.

ECU60 is used to control the driving of toroidal continuously variable transmission 1; Be used to control change gear particularly; At this,, carry out the operation control of motor 21 also based on various input signals or the various mapping imported from the sensor everywhere that is installed in the vehicle 1A that is provided with motor 21; The throttle valve opening control of the not shown throttle valve of the suction air quantity of for example, the injection of not shown Fuelinjection nozzle control, control motor 21, the IGNITION CONTROL of spark plug etc.And, ECU60 control according to the running state of toroidal continuously variable transmission 1 toroidal continuously variable transmission 1 each one driving and control actual gear ratio, actual gear ratio is the gear ratio of the reality of toroidal continuously variable transmission 1.Promptly, ECU60 is through confirming the target change gear ratio as the gear ratio of target based on running state such as engine speed that for example various sensor detected, throttle valve opening, accelerator opening, input speed, output speed, gear or tilt angle, path increment etc.; And drive gear ratio change portion 5 and make live roll 4 from the neutral position to shift position side shifting to predetermined path increment and vert to predetermined tilt angle, carry out the change of gear ratio.Furthermore; ECU60 is through carrying out dutycycle control based on control command value to the driving current of the flow control valve that offers hydraulic pressure control device 9; Control first OP1 of hydraulic chamber of hydraulic piston portion 8, the oil pressure of second OP2 of hydraulic chamber; Make live roll 4 with gudgeon 6 from the neutral position to shift position side shifting to predetermined path increment and vert to predetermined tilt angle, thereby actual gear ratio is controlled to be target change gear ratio.

Particularly, this ECU60 is connected with various sensor electrical such as tilt angle sensor 50, stroke sensor 51, engine rotation speed sensor 52, input speed sensor 53, output speed sensor 54, accel sensor 55, vehicle speed sensor 56, throttle valve opening sensor 57, working oil temperature sensor 58, pipeline pressure sensors 59.In addition, aspect concept of function, ECU60 is provided with torque-converters control device 61, forward-reverse conversion control device 62, clamping pressure control device 63, engine control portion 64, gear ratio control device 65.

At this, it is processing division 60a, memory section 60b and the 60c of input output portion that the center constitutes that ECU60 has with the microcomputer, and these parts interconnect, and can exchange signal each other.Driving comprises that not shown drive circuit and the above-mentioned various sensors of various piece of the vehicle 1A of toroidal continuously variable transmission 1 are connected with the 60c of input output portion, the 60c of this input output portion and these sensors etc. between carry out the input output of signal.In addition, store the computer program of the various piece of control toroidal continuously variable transmission 1 among the memory section 60b.This memory section 60b can (Random Access Memory: random access memory) volatile memory or they constitutes by nonvolatile memories (storage medium that CD-ROM etc. only can read) such as hard disk unit, magneto-optical disc apparatus or flash memory, RAM.Processing division 60a is by not shown storage and CPU (Central Processing Unit: central processing unit (CPU)) constitute, and have above-mentioned torque-converters control device 61, forward-reverse conversion control device 62, clamping pressure control device 63, engine control portion 64, gear ratio control device 65 at least.Said computer program is read in the storage that is assembled among this processing division 60a carry out computing and transmit control signal based on being arranged on the result that sensor detected on the various piece through processing division 60a, thereby carry out various controls based on ECU60 according to the result of computing.At this moment, the numerical value that processing division 60a will store in the calculating process takes the circumstances into consideration to store into memory section 60b, and the numerical value that reads storage carries out computing.In addition, when controlling the various piece of this toroidal continuously variable transmission 1, also can replace said computer program and use the specialized hardware that is different from ECU60 to control.

Tilt angle sensor 50 detects the tilt angle of live roll 4 with respect to input disk 2 and output disk 3, and sends detected tilt angle to ECU60.In addition, with a plurality of live rolls 4 a plurality of tilt angle sensors 50 are set accordingly, tilt angle sensor 50 detects the tilt angle of each live roll 4 respectively.At this, the tilt angle conduct that tilt angle sensor 50 is detected is to be detected around the angle of swing of spin axis X3 around the gudgeon 6 that spin axis X3 is rotated with live roll 4.

Stroke sensor 51 detects the path increment of live roll 4, and sends the path increment that detects to ECU60.In addition, stroke sensor 51 and a plurality of live rolls 4 correspondingly are provided with a plurality of, and detect the path increment of each live roll 4 respectively.At this, the path increment conduct of the live roll 4 that stroke sensor 51 is detected with this live roll 4 to be detected along the path increment of the gudgeon 6 that moves on the direction of spin axis X3.

In addition, engine rotation speed sensor 52 detection of engine rotating speeds are as the rotational speed of motor 21, and send the engine speed that detects to ECU60, and motor 21 is driving sources.At this; Engine rotation speed sensor 52 for example can use the crankshaft angle sensor of the crankshaft angles of detection of engine; ECU60 differentiates intake stroke, compression stroke, expansion stroke, exhaust stroke in each cylinder based on the crankshaft angles that detects, and calculates the rotational speed of engine speed (rpm) as motor.In addition, at this, engine speed is in other words corresponding with the rotational speed of bent axle 21a, if the rotational speed of this bent axle 21a is big more, then the rotating speed of bent axle 21a, engine speed are also big more.Below, as long as do not specify that rotational speed is described to rotating speed.

Input speed sensor 53 detects input speed and the sense of rotation as the rotating speed of input disk 2, and sends input speed and the sense of rotation that detects to ECU60.Output speed sensor 54 detects output speed and the sense of rotation as the rotating speed of output disk 3, and sends output speed and the sense of rotation that detects to ECU60.In addition, input speed sensor 53, output speed sensor 54 also can be respectively detect based on the rotating speed of the parts that are rotated with the proportional rotating speed of rotating speed (rotational speed) (rotational speed) with input disk 2, output disk 3.In addition, input speed, output speed are in other words corresponding with the rotational speed of input disk 2, output disk 3.

Accel sensor 55 detects the accelerator opening of the vehicle 1A that this toroidal continuously variable transmission 1 is installed, and sends the accelerator opening that detects to ECU60.Vehicle speed sensor 56 detects the speed of a motor vehicle of the vehicle 1A that this toroidal continuously variable transmission 1 is installed, and sends the speed of a motor vehicle that detects to ECU60.Throttle valve opening sensor 57 detects the throttle valve opening of the vehicle 1A that this toroidal continuously variable transmission 1 is installed, and sends the throttle valve opening that detects to ECU60.

Working oil temperature sensor 58 detects the temperature of the working oil that is applied to this toroidal continuously variable transmission 1, and sends the working oil temperature that detects to ECU60.Pipeline pressure sensor 59 detects as the pipeline of the initial pressure of hydraulic pressure control device 9 and presses, and sends the pipeline that detects to ECU60 and press.

The lock-up clutch of torque-converters control device 61 control torque-converters 22.Torque-converters control device 61 is carried out joint and the releasing of joint of the lock-up clutch of torque-converters 22 through control hydraulic pressure control device 9, that is, carry out joints/disconnection and control.

Forward-reverse conversion control device 62 control forward-reverse shifting mechanisms 23.Forward-reverse conversion control device 62 is carried out the conversion control of forward-reverse shifting mechanism 23 through hydraulic pressure control device 9 being controlled forward gear clutch and the joint of reversing break and releasing, i.e. the execution joint/disconnection control of joint of carrying out forward-reverse shifting mechanism 23.

Clamping pressure control device 63 control actions are clipped in live roll 4 the oil pressure pressing mechanism 15 of the clamping pressure between input disk 2 and the output disk 3.In other words, the surface of contact of clamping pressure control device 63 control actions on the contact segment of the surface of contact 4a of

ring surface

2a, 3a and the live roll 4 of input disk 2, output disk 3 pressed.Clamping pressure control device 63 is through controlling the amount that produces the working oil of the 15a of hydraulic chamber supply with control to clamping pressure to hydraulic pressure control device 9; Thereby will be controlled to be based on the clamping pressure of oil pressure pressing mechanism 15 based on expected objective clamping pressure, be made as based on predetermined face pressure the surface of contact on the contact segment of the surface of contact 4a of the

ring surface

2a, 3a and the live roll 4 that act on input disk 2, output disk 3 is voltage-controlled to the input torque of toroidal continuously variable transmission 1 to the input torque of toroidal continuously variable transmission 1.

The operation of engine control portion 64 control motors 21.Engine control portion 64 controls the output that obtains from motor 21 through control sparger, spark plug, electronic throttle, and execution is as the engine torque of the output torque of motor 21 and the control of engine speed.

Gear ratio control device 65 control gear ratio change portions 5 make that the actual gear ratio as the gear ratio of reality becomes the target change gear ratio as the gear ratio of target.In other words, gear ratio control device 65 is controlled actual gear ratio through control gear ratio change portion 5, and feasible input speed to the reality of importing disk 2 becomes the target input speed corresponding to target change gear ratio.Promptly; As stated; Gear ratio control device 65 is through confirming the target change gear ratio as the gear ratio of target based on running state such as engine speed, throttle valve opening, accelerator opening, engine speed, input speed, output speed, gear or tilt angle, path increment etc.; And drive gear ratio change portion 5 and make live roll 4 from the neutral position to the shift position side shifting to predetermined path increment and rotate to predetermined tilt angle, carry out the change of gear ratio.

In above-mentioned toroidal continuously variable transmission 1, if driving force (torque) is imported into input disk 2, then driving force is transmitted to the live roll that contacts with this input disk 2 via traction 4, and driving force is transmitted to output disk 3 from this live roll 4 via traction.During this period; Traction is pressurized and carry out glass transition; And come transmission of drive force through the big shearing of following therewith, therefore respectively import disk 2, output disk 3 is pushed by oil pressure pressing mechanism 15, make they with live roll 4 between generation corresponding to the clamping pressure of input torque.In addition; Because the peripheral velocity of live roll 4 is identical in fact with the peripheral velocity of the torque transmission point (point of contact that live roll 4 contacts via traction) of each input disk 2, output disk 3; Therefore; According to the point of contact of input disk 2 and live roll 4 based on the point of contact of the radius of spin axis X1 and live roll 4 and output disk 3 radius based on spin axis X1; Each imports rotating speed (rotational speed) difference of disk 2, output disk 3, thereby the ratio of their rotating speed (rotational speed) becomes gear ratio.

And; The gear ratio control device 65 of ECU60 is when changing to gear ratio the target change gear ratio of setting, when carrying out the speed change of gear ratio; Sense of rotation based on input disk 2 (perhaps output disk 3); To the flow control valve of hydraulic pressure control device 9 supply driving current, controlling the oil pressure of first OP1 of hydraulic chamber, second OP2 of hydraulic chamber, thereby before live roll 4 reaches the tilt angle corresponding to target change gear ratio, gudgeon 6 is moved from the neutral position to first direction A1 or second direction A2.For example; If along the oil pressure through first OP1 of hydraulic chamber under the state of the rotation of the arrow B direction (counterclockwise) among Fig. 4 live roll 4 is moved at input disk 2 from the neutral position to the first direction A1 along spin axis X3, then gear ratio increase and execution lower category as stated.On the other hand; If along the oil pressure through second OP2 of hydraulic chamber under the state of the rotation of the arrow B direction (counterclockwise) among Fig. 4 live roll 4 is moved at input disk 2 from the neutral position to the second direction A2 along spin axis X3, then gear ratio reduces and carries out to upgrade as stated.In addition, when the gear ratio of setting is fixed, before live roll 4 reaches the neutral position once more, gudgeon 6 is moved to first direction A1 or second direction A2.

In addition; The gear ratio control device 65 of this ECU60 is for example carried out the cascade feedback control based on the tilt angle of the live roll 4 that is detected by tilt angle sensor 50 and by the path increment that stroke sensor 51 detects, and makes actual gear ratio (actual gear ratio) become target change gear ratio (gear ratio of the target after the speed change).Promptly; This ECU60 confirms the target tilt angle of corresponding with the target change gear ratio tilt angle as target based on accelerator opening and the speed of a motor vehicle; And be the target stroke amount that deviation between the actual tilt angle is confirmed corresponding with target change gear ratio, the target tilt angle path increment as target based on this target tilt angle and by the tilt angle of the reality of tilt angle sensor, and the hydraulic pressure control device 9 of control moving part 7 makes the path increment that stroke sensor detected become this target stroke amount.

That is, the gear ratio control device 65 of ECU60 is confirmed the target change gear ratio as the gear ratio of target according to the accelerator opening and the speed of a motor vehicle etc.At this; For example; Based on requiring the driven quantity and the speed of a motor vehicle to calculate to require driving force by expressions such as accelerator openings; And require the driving force and the speed of a motor vehicle to obtain target output by this, and obtain the rotating speed of realizing the motor of this target output with the oil consumption rate of minimum, and to obtain the rotating speed that target change gear ratio makes input speed to toroidal continuously variable transmission 1 become the target suitable with the rotating speed of this motor be the target input speed.And, if know the point of contact between live roll 4 and input disk 2 and the output disk 3, then only just can confirm the relation between gear ratio and the tilt angle through the geometry shape, therefore can obtain the target tilt angle by target change gear ratio.

In addition; In the speed Control of toroidal continuously variable transmission 1 so; Basically, only the tilt angle (in other words, gear ratio) by the tilt angle sensor being carried out feedback control gets final product; But because path increment is equivalent to the differential of tilt angle, the attenuating of the vibration in the control that also can realize suppressing verting through the feedback control of the path increment that combines to detect by stroke sensor.In addition, in order to improve the responsiveness of gear ratio, the gear ratio control device 65 of this ECU60 also can combine this feedback control and feedforward control.

Yet the hydraulic pressure control device 9 of the toroidal continuously variable transmission 1 of this mode of execution comprises pump-unit 92 as stated.As shown in Figure 1, the pump-unit 92 of this mode of execution be can multistage ground conversion working oil to the so-called ejection volume-variable formula pump-unit of the ejection capacity of control system 90A.

At this, the control system 90A in the hydraulic pressure control device 9 of toroidal continuously variable transmission 1 controls at least through the pressure of working oil that surface of contact between the surface of contact 4a of

ring surface

2a, 3a and live roll 4 of input disk 2, output disk 3 is pressed and as the gear ratio of input disk 2 with the rotational speed ratio of output disk 3.That is, the control system 90A of this mode of execution is constituted as and comprises the above-mentioned oil pressure pressing mechanism 15 that changes the above-mentioned gear ratio change portion 5 of gear ratio and change the surface of contact pressure of

ring surface

2a, 3a and surface of contact 4a through the oil pressure that produces the working oil of the 15a of hydraulic chamber supply to clamping pressure through the oil pressure to the working oil of speed Control hydraulic chamber 82 supply at least.

Particularly, the hydraulic pressure control device 9 of this mode of execution comprises food tray 91, pump-unit 92, filter 93, a plurality of

oil circuit

94a, 94b, 94c, 94d, 94e, 94f, 94g, 94h, 94i, open and close valve 95a, safety check 95b, safety valve 95c.

Food tray 91 is storage units, and it is used to store the traction as working oil.

The pump-unit 92 of this mode of execution can multistage ground (being 2 grades here) conversion working oil to the ejection capacity of control system 90A.Pump-unit 92 has main pump 96 as the 1st pump, as the auxiliary pump 97 of the 2nd pump and as the transfer valve 98 of converter unit.

Rotation with the bent axle 21a of motor 21 synchronously drives main pump 96 with auxiliary pump 97, and can be in the working oil of back ejection suction of boosting.That is, main pump 96 and auxiliary pump 97 drive linkedly and can pressurize to working oil through the rotation with the bent axle 21a of the motor 21 that produces driving force.The ejection capacity of main pump 96 and auxiliary pump 97 about equally, perhaps the ejection capacity of main pump 96 is set at the ejection capacity greater than auxiliary pump 97.In addition; Main pump 96, auxiliary pump 97 have following tendency: the rotating speed of bent axle 21a that drives the motor 21 of this main pump 96, auxiliary pump 97 is that engine speed is high more; The ejection flow of main pump 96, auxiliary pump 97 is just many more, and engine speed is more little, and the ejection flow of main pump 96, auxiliary pump 97 is just few more.

In addition; The pump-unit 92 of this mode of execution is described to use motor 21 as driving source, but the invention is not restricted to this, also can use the special-purpose motor of this pump-unit 92 etc. as driving source; In addition, also can independent driving source be set respectively to main pump 96 and auxiliary pump 97.

The working oil that main pump 96 sucks to control system 90A ejection.Main pump 96 sucks oil circuit 94a at the suction port of working oil and first and links, this first suck oil circuit 94a with after state second suck that oil circuit 94c links and second suck oil circuit 94c and

filter

93 and 91 interior connections of food tray via this.In addition, main pump 96 links at the ejiction opening of working oil and the first ejection oil circuit 94b, and this first ejection oil circuit 94b is communicated with control system 90A as high-pressure system.Main pump 96 sucks oil circuit 94c and first via filter 93, second and sucks the working oil in the oil circuit 94a suction food tray 91, and in the working oil of back to the first ejection oil circuit 94b ejection suction of boosting.

At this; Filter 93 be used at pump-unit 92 main pump 96, after the auxiliary pump 97 stated via first suck oil circuit 94a, after state second suck oil circuit 94c when sucking the working oil in the food tray 91, from be inhaled into first working oil that suck oil circuit 94a, the second suction oil circuit 94c, leach foreign matter.

Auxiliary pump 97 is used for to control system 90A or is different from the working oil that ejection sucks as the lubrication system 90B of supply system of control system 90A.Auxiliary pump 97 sucks oil circuit 94c binding at the suction port and second of working oil, and this second suction oil circuit 94c is via being communicated with in filter 93 and the food tray 91.In addition, auxiliary pump 97 links at the ejiction opening and the second ejection oil circuit 94d of working oil, and this second ejection oil circuit 94d links with control system ejection oil circuit 94e and lubrication system ejection path 94f via transfer valve 98.Control system ejection oil circuit 94e links with the first ejection oil circuit 94b and first sprays oil circuit 94b and be communicated with control system 90A as high-pressure system via this.Lubrication system ejection path 94f is communicated with lubrication system 90B as low service system.Auxiliary pump 97 sucks the working oil in the oil circuit 94c suction food tray 91 via filter 93 and second, and is boosting after spray the working oil that sucks by the second ejection oil circuit 94d to control system ejection oil circuit 94e or lubrication system ejection path 94f.

Transfer valve 98 for example is constituted as and comprises solenoid valve etc., and can spray the destination that is connected of the conversion second ejection oil circuit 94d between oil circuit 94e and the lubrication system ejection path 94f in control system.That is, transfer valve 98 can be between control system 90A and lubrication system 90B the ejection destination of the working oil in the conversion auxiliary pump 97.

At this, transfer valve 98 is connected with ECU60, and passes through the driving of this ECU60 control change valve 98.Transfer valve 98 for example is made up of following solenoid valve; When solenoid 98a switches on (when connecting control); This solenoid valve is in the state that connects the second ejection oil circuit 94d and control system ejection oil circuit 94e; On the other hand, when solenoid 98a no electric circuit (when breaking off control), this solenoid valve is in the state that connects the second ejection oil circuit 94d and lubrication system ejection path 94f.Transfer valve 98 for example is constituted as and comprises solenoid 98a and elastic member 98b.If the driving current to solenoid 98a supply is set to prearranging quatity; The pressing force that is produced by solenoid 98a that then acts on the not shown valve core of the spool valve makes valve core of the spool valve move to the ON position greater than acting on the bias force that is produced by elastic member 98b on this valve core of the spool valve; Thereby transfer valve 98 becomes ON state (state of the ON part shown in Fig. 1); That is, the second ejection oil circuit 94d and the connected state of control system ejection oil circuit 94e.For example; If the driving current to solenoid 98a supply is set to 0A; The pressing force that is produced by solenoid 98a that then acts on the not shown valve core of the spool valve makes valve core of the spool valve move to the OFF position less than acting on the bias force that is produced by elastic member 98b on this valve core of the spool valve; Thereby transfer valve 98 becomes OFF state (state of the OFF part shown in Fig. 1), that is, and and the second ejection oil circuit 94d and the connected state of lubrication system ejection path 94f.In addition; Transfer valve 98 is not limited thereto form; For example; Also can press to the control oil pressure of valve core of the spool valve effect to the ON position side based on pipeline, the pressing force that this control oil pressure produces makes valve core of the spool valve move to the ON position greater than acting on the bias force that is produced by elastic member 98b on this valve core of the spool valve, sprays the connected state of oil circuit 94e thereby become the second ejection oil circuit 94d with control system.

At this, control system 90A is the supply destination that so-called pipeline is pressed, and is constituted as as stated and comprises gear ratio change portion 5 and oil pressure pressing mechanism 15.That is, hydraulic pressure control device 9 produces the flow control valve (not shown) etc. of the flow of the 15a of hydraulic chamber at the flow control valve (not shown) of pressing the flow that is provided with the speed Control hydraulic chamber 82 of adjustment working oil in gear ratio change portion 5 in the supply system to the pipeline of this control system 90A or the clamping pressure of adjustment working oil in oil pressure pressing mechanism 15.In addition, lubrication system 90B is so-called lubricated oil supplying destination, and for example is constituted as the slide part of the toroidal continuously variable transmissions such as contacting part 1 that comprise that exchanging shaft 11 or ring surface 2a, 3a contact with surface of contact 4a.That is, hydraulic pressure control device 9 is at the above-mentioned nozzle 17d (with reference to Fig. 4) that in the lubricating oil supply system of this lubrication system 90B supplying lubricating oil, is provided with the supplies such as contacting part that working oil is contacted with surface of contact 4a to exchanging shaft 11 or ring surface 2a, 3a as lubricant oil etc.For this control system 90A and lubrication system 90B, control system 90A is the system of relative elevated pressures, and lubrication system 90B is the system of relatively low pressure.That is,, press the pressure of the working oil of supply system to be set to the relatively big pressure of pressure of the working oil of the lubricating oil supply system of comparing lubrication system 90B to the pipeline of control system 90A basically for control system 90A and lubrication system 90B.

In addition, this hydraulic pressure control device 9 is provided with according to running state and supplies work oil supplying oil circuit 94g from control system 90A to lubrication system 90B, and this supply oil circuit 94g is provided with open and close valve 95a.This open and close valve 95a is a solenoid valve, and is connected with ECU60, through this ECU60 controlling and driving.Open and close valve 95a is closing the circulation of sealing supply oil circuit 94g under the valve state and blocking working oil, and on the other hand, open and close valve 95a is opening the circulation of opening supply oil circuit 94g under the valve state and allowing working oil.

In addition, the first ejection oil circuit 94b and the second ejection oil circuit 94d link through linking oil circuit 94h, and this binding oil circuit 94h is provided with safety check 95b.This safety check 95b allows the circulation of working oil from the second ejection oil circuit 94d side direction, the first ejection oil circuit 94b side through making the second ejection oil circuit 94d side become predetermined oil pressure in linking oil circuit 94h; On the other hand, this safety check 95b stops the circulation of working oil from the first ejection oil circuit 94b side direction, the second ejection oil circuit 94d side.

In addition, lubrication system ejection path 94f and second sucks oil circuit 94c and links through release oil circuit 94i, and release oil circuit 94i is provided with safety valve 95c.Safety valve 95c is used for promptly sucking oil circuit 94c side from lubrication system ejection path 94f side direction second and returning to the pressure of the working oil of lubrication system ejection path 94f ejection the downstream side from the remaining working oil of this auxiliary pump 97 ejections from auxiliary pump 97 being returned via the second ejection oil circuit 94d from auxiliary pump 97 to upstream side.Therefore, this hydraulic pressure control device 9 is with lubrication system 90B, here for lubrication system ejection path 94f maintains the pressure below the predetermined pressure, basically this lubrication system 90B maintained the low pressure of comparing with control system 90A.

Through transfer valve 98 the ejection destination of the working oil in the auxiliary pump 97 is transformed to control system 90A from lubrication system 90B, the pump-unit 92 that constitutes as stated can transform to big relatively capacity to the ejection capacity of control system 90A from relatively little capacity with working oil.Promptly; Through transfer valve 98 the ejection destination of the working oil in the auxiliary pump 97 is transformed to control system 90A from lubrication system 90B, pump-unit 92 can be with two-step way working oil that pump-unit 92 is all to the ejection capacity of control system 90A from only transforming to ejection capacity (big relatively capacity) based on main pump 96 and auxiliary pump 97 based on the ejection capacity (relatively little capacity) of the main pump 96 main pump 96, the auxiliary pump 97.

Here, the ECU60 of this mode of execution is provided with conversion control device 66 concept of function on processing division 60a.This conversion control device 66 is through according to the running state of the vehicle 1A that toroidal continuously variable transmission 1 and motor 21 are installed to the driving of transfer valve 98 (for example; Driving current to solenoid 98a supply) controls, 92 pairs of working oil of pump-unit are controlled to the conversion of the ejection capacity of control system 90A.Conversion control device 66 can come the conversion destination of control change valve 98 according to the vehicle 1A that toroidal continuously variable transmission 1 and motor 21 are installed, and, can control the connection destination of the second ejection oil circuit 94d that is.In addition, here, conversion control device 66 can also be controlled the switching of open and close valve 95a.

For example; Conversion control device 66 is based on the working oil of main pump 96 during to the necessary flow of the ejection flow of control system 90A required working oil in more than or equal to control system 90A; The driving of control change valve 98; Make the second ejection oil circuit 94d and lubrication system ejection path 94f be in coupled condition, and the ejection destination of auxiliary pump 97 is transformed to the lubrication system 90B as relatively low pressure system.In other words; When necessary flow from the ejection flow of main pump 96 to the working oil of control system 90A that can bear fully based on; The driving of conversion control device 66 control change valves 98; Make the second ejection oil circuit 94d be in the state that is connected, and the ejection destination of auxiliary pump 97 is transformed to the lubrication system 90B as relatively low pressure system with lubrication system ejection path 94f.That is, main pump 96 after the working oil suction and pressurization with food tray 91, sprays this working oil from suck oil circuit 94a to the first ejection oil circuit 94b.In addition, auxiliary pump 97 after the oil suction and pressurization with food tray 91, sprays path 94f ejection via the second ejection oil circuit 94d to lubrication system from suck oil circuit 94c.Therefore, this hydraulic pressure control device 9 is supplied to the control system 90A as high-pressure system with the working oil that main pump 96 is sprayed, and on the other hand, this hydraulic pressure control device 9 is supplied to the lubrication system 90B as low service system with the working oil that auxiliary pump 97 is sprayed.

Thus; This hydraulic pressure control device 9 is through arriving the ejection destination setting of auxiliary pump 97 the lubrication system 90B of low service system; For example; Be set to as the situation of the state of the control system 90A of high-pressure system with the ejection destination of continuing auxiliary pump 97 and compare, can suppress the workload of auxiliary pump 97 and can suppress the driving torque of auxiliary pump 97.That is, the pump load (pump drives loss) in the auxiliary pump 97 can be reduced, consequently, for example oil consumption rate can be improved.In addition, conversion control device 66 open and close valve 95a is in closes valve state and sealing supply oil circuit 94g, thereby the blocking-up working oil is via the circulation of supply oil circuit 94g when as above through transfer valve 98 the ejection destination of auxiliary pump 97 being transformed to lubrication system 90B.

In addition; For example; Conversion control device 66 for example needs a large amount of working oil and only uses working oil based on main pump 96 when the ejection flow of control system 90A can not satisfy the necessary flow of the required working oil of control system 90A in control system 90A; Driving to transfer valve 98 is controlled, and makes the second ejection oil circuit 94d and control system ejection oil circuit 94e be in coupled condition, and the ejection destination of auxiliary pump 97 is relatively transformed to control system 90A.That is, main pump 96 working oil of food tray 91 is sucked from suck oil circuit 94a and the pressurization back, to the first ejection oil circuit 94b ejection.In addition, auxiliary pump 97 sucks the oil of food tray 91 and the back of pressurizeing, sprays oil circuit 94b ejection to the second ejection oil circuit 94d ejection and via control system ejection oil circuit 94e to first from suck oil circuit 94c.Therefore, the working oil that sprayed of main pump 96, auxiliary pump 97 all is supplied to the control system 90A as high-pressure system.

Thus; This hydraulic pressure control device 9 can carry out the supply of working oil to control system 90A through main pump 96 and auxiliary pump 97; Therefore, can suppress with respect to the working oil among the control system 90A necessary flow, to the situation of the discharging jet quantity not sufficient of the working oil of the reality of control system 90A.In addition; Conversion control device 66 is when so transforming to control system 90A through transfer valve 98 with the ejection destination of auxiliary pump 97; Open the circulation that supply oil circuit 94g allows working oil through making open and close valve 95a be in out the valve state, thereby via the working oil of supply oil circuit 94g to lubrication system 90B supply control system 90A.Thus, toroidal continuously variable transmission 1 can prevent under-supply to lubrication system 90B of in hydraulic pressure control device 9 working oil.

Here; For example; Example as shown in Figure 7; In the hydraulic pressure control device 9 that is constituted as the pump-unit 92 that comprises such ejection capacity variable type, the engine speed NE of motor 21 more than or equal to the regional T1 of predetermined engine speed NE1 in the ejection flow of main pump 96 more relatively, therefore basically the ejection destination of auxiliary pump 97 is transformed to the lubrication system 90B as low service system.Here; In Fig. 7; Transverse axis representes to be equipped with the speed V (Km/h) of the vehicle 1A of toroidal continuously variable transmission 1; The longitudinal axis representes to be equipped with the engine speed NE (rpm) of motor 21 of the vehicle 1A of toroidal continuously variable transmission 1, and γ max representes the corresponding shift cable of maximum gear ratio with toroidal continuously variable transmission 1, and γ min representes the corresponding shift cable of minimum gear ratio with toroidal continuously variable transmission 1.Predetermined engine speed NE1 for example be can guarantee based on the working oil of the main pump 96 that drives by motor 21 to the ejection flow of control system 90A more than or equal to control system 90A in the engine speed of necessary flow of needed working oil.

Promptly; In this case; Conversion control device 66 is for example at the engine speed NE of the motor 21 that drives main pump 96 during more than or equal to predetermined engine speed NE1 (when the relation of engine speed NE and speed V is positioned at regional T1 in the current running state); Through transfer valve 98 the ejection destination of auxiliary pump 97 is transformed to the lubrication system 90B as low service system, reduce the pump load (pump drives loss) in the auxiliary pump 97 and realize the improvement of oil consumption rate.On the other hand; Conversion control device 66 is for example at engine speed NE during less than predetermined engine speed NE1 under (when the relation of engine speed NE and speed V is positioned at regional T2 in the current running state); Basically through transfer valve 98 the ejection destination of auxiliary pump 97 is transformed to the control system 90A as high-pressure system, can suppress with respect to the necessary flow of the working oil among the control system 90A situation to the discharging jet quantity not sufficient of the working oil of the reality of control system 90A.In addition; The benchmark engine speed NE0 on the border that be positioned at low engine speed side of zone among the T2 is the engine speed of benchmark that constitutes the driving of main pump 96, auxiliary pump 97; And be the minimum engine speed under the common running state of motor 21, near the rotating speed the racing speed for example.

But; In the hydraulic pressure control device 9 that is constituted as the pump-unit 92 that comprises such ejection capacity variable type; For example, under the situation of engine speed NE, also can reduce pump load (pump drives loss) and further improve oil consumption rate even hope less than predetermined engine speed NE1.That is, in such hydraulic pressure control device 9, hope to enlarge through transfer valve 98 the ejection destination of auxiliary pump 97 is transformed to the operation area that the lubrication system 90B as low service system can reduce pump load (pump drives loss) and improve oil consumption rate.On the other hand; In such hydraulic pressure control device 9; For example; Less than predetermined engine speed NE1, through transfer valve 98 the ejection destination setting of auxiliary pump 97 is suppressed necessary flow working oil with respect to the working oil among the control system 90A under the situation of the discharging jet quantity not sufficient of control system 90A to the control system 90A as high-pressure system, even the situation of working oil to the discharging jet quantity not sufficient of control system 90A for example possibly take place also when the urgent speed change of toroidal continuously variable transmission 1 etc. at engine speed NE.That is, in the hydraulic pressure control device 9 that constitutes the pump-unit 92 that comprises such ejection capacity variable type, hope according to running state conversion ejection capacity suitably.

Therefore; Even engine speed NE is less than predetermined engine speed NE1; Based on the working oil of main pump 96 under the ejection flow of control system 90A can be born the state of the necessary flow of needed working oil among the control system 90A, running state that the vehicle 1A of toroidal continuously variable transmission 1 is installed is under the situation near the state of steady operational status; The necessary flow of needed working oil in fact can be seldom among the control system 90A; Therefore the hydraulic pressure control device 9 of this toroidal continuously variable transmission 1 arrives the lubrication system 90B as low service system through using transfer valve 98 with the ejection destination setting of auxiliary pump 97, and realization can reduce pump load (pump drives loss) and improve the expansion of the operation area of oil consumption rate.

In addition; The hydraulic pressure control device 9 of the toroidal continuously variable transmission 1 of this mode of execution at least through pump-unit 92 to the ejection capacity of control system 90A ejection working oil along with speed change when relatively little capacity transforms to big relatively capacity; Promptly; Use transfer valve 98 with the ejection destination of auxiliary pump 97 when the lubrication system 90B as low service system transforms to the control system 90A as high-pressure system; Through control system 90A is controlled speed change is delayed relatively, thus suppress with respect to the working oil among the control system 90A when the urgent speed change of toroidal continuously variable transmission 1 necessary flow, to the situation of the discharging jet quantity not sufficient of the working oil of the reality of control system 90A.

In addition; In following explanation; As long as do not specify that in pump-unit 92, the ejection destination of auxiliary pump 97 is set to the state as the lubrication system 90B of low service system; That is the state that, is merely the main pump 96 in main pump 96, the auxiliary pump 97 to the ejection source of the working oil of control system 90A is called " 1 ejection state ".On the other hand, in pump-unit 92, the ejection destination of auxiliary pump 97 is set to the state as the control system 90A of high-pressure system, that is, be main pump 96 and both states of auxiliary pump 97 are called " 2 ejection state " to the ejection source of the working oil of control system 90A.

Particularly, will be set to relatively little capacity to the ejection capacity of control system 90A ejection working oil at engine speed NE through pump-unit 92 during more than or equal to predetermined engine speed NE1 as stated as the conversion control device 66 of the conversion control unit of this mode of execution.Promptly; Conversion control device 66 is when judging current engine speed NE more than or equal to predetermined engine speed NE1; Through transfer valve 98 with the ejection destination setting of auxiliary pump 97 to lubrication system 90B as low service system, make working oil be in 1 ejection state based on main pump 96 to the ejection state of control system 90A.

In addition; Conversion control device 66 is at engine speed NE during less than predetermined engine speed NE1 and the running state that the vehicle 1A of toroidal continuously variable transmission 1 is installed when being in the state near steady operational status; To be set to relatively little capacity to the ejection capacity of control system 90A ejection working oil through pump-unit 92; On the other hand; When running state is in the state near the astable operation state, will be set to big relatively to the ejection capacity of control system 90A ejection working oil through pump-unit 92.Promptly; Conversion control device 66 is when judging that current engine speed NE is in the state near steady operational status less than predetermined engine speed NE1 and the running state of judging vehicle 1A; Through transfer valve 98 with the ejection destination setting of auxiliary pump 97 to lubrication system 90B as low service system; Make working oil be in 1 ejection state based on main pump 96 to the ejection state of control system 90A; On the other hand; Conversion control device 66 when judging that current engine speed NE is in the state near the astable operation state less than predetermined engine speed NE1 and the running state of judging vehicle 1A, through transfer valve 98 with the ejection destination setting of auxiliary pump 97 to control system 90A as high-pressure system, make working oil be in 2 ejection states based on main pump 96 and auxiliary pump 97 to the ejection state of control system 90A.Here, conversion control device 66 can be steady operational status or unsteady state based on the testing signal of various sensors or to the running state of the judgement current vehicles 1A such as control signal of the each several part of the vehicle 1A that comprises toroidal continuously variable transmission 1 for example.

Consequently; Even engine speed NE is less than predetermined engine speed NE1; Be under the situation near the state of steady operational status in the running state of the vehicle 1A that toroidal continuously variable transmission 1 is installed; The hydraulic pressure control device 9 of toroidal continuously variable transmission 1 also through transfer valve 98 with the ejection destination setting of auxiliary pump 97 to will being set to relatively little capacity to the ejection capacity of control system 90A ejection working oil through pump-unit 92 as the lubrication system 90B of low service system, thereby can reduce based on the pump load (pump drives loss) of auxiliary pump 97 and further improve oil consumption rate.Therefore; When the hydraulic pressure control device 9 of toroidal continuously variable transmission 1 is in the state near the astable operation state at engine speed NE less than predetermined engine speed NE1 and running state that the vehicle 1A of toroidal continuously variable transmission 1 is installed; Through transfer valve 98 with the ejection destination setting of auxiliary pump 97 to being set to big relatively capacity to the ejection capacity of control system 90A ejection working oil through pump-unit 92 as the lubrication system 90B of low service system, can suppress with respect to the working oil among the control system 90A necessary flow, to the situation of the discharging jet quantity not sufficient of the working oil of the reality of control system 90A.Thus, the hydraulic pressure control device 9 of toroidal continuously variable transmission 1 can be according to the ejection capacity of suitably conversion working oil of running state.

And; As the gear ratio control device 65 of gear ratio control unit at least through pump-unit 92 to the ejection capacity of control system 90A ejection working oil along with speed change when relatively little capacity transforms to big relatively capacity; Promptly; When using transfer valve 98 that the ejection destination of auxiliary pump 97 is transformed to the control system 90A as high-pressure system, carry out control system 90A is controlled and speed change that speed change is delayed relatively delays control.Preferably, gear ratio control device 65 begun to transform to from the conversion of the ejection capacity of pump-unit 92 to the ejection capacity of the reality of pump-unit 92 big relatively capacity during carry out this speed change and delay control.In addition; The gear ratio control device 65 of this mode of execution be not limited to when urgent speed change also can working oil to the ejection state of control system 90A from based on 1 ejection state transformation of main pump 96 to based on 2 ejection states of main pump 96 and auxiliary pump 97 time, control system 90A controlled delay relatively when making the common speed change of gear ratio.

Here; The conversion elapsed time point of the ejection capacity of pump-unit 92 is for example to have exported the time point that sprays the transformation directive of capacity from conversion control device 66 to pump-unit 92, and the conversion concluding time point of the ejection capacity of pump-unit 92 is to the actual time point that increases to the total ejection flow of main pump 96 and auxiliary pump 97 of the ejection flow of control system 90A ejection working oil through pump-unit 92.Gear ratio control device 65 can be judged the conversion concluding time point of the ejection capacity of this pump-unit 92 to working oil through sensor (not shown) etc. to the measured value of the ejection flow of control system 90A, also can based on whether have passed through the conversion concluding time point of the ejection capacity that the predefined scheduled time judges this pump-unit 92 from conversion elapsed time point.Promptly; Gear ratio control device 65 in advance through grasps such as test from conversion elapsed time of the ejection capacity of pump-unit 92 point until through pump-unit 92 to control system 90A ejection working oil scheduled time of time point of the actual total ejection flow that increases to main pump 96 and auxiliary pump 97 of ejection flow; And this scheduled time is stored among the memory section 60b, gear ratio control device 65 will pass through the time point of the above-mentioned scheduled time from conversion elapsed time point and be estimated as conversion concluding time point.

Consequently; The hydraulic pressure control device 9 of toroidal continuously variable transmission 1 through pump-unit 92 to the ejection capacity of control system 90A ejection working oil along with speed change when relatively little capacity transforms to big relatively capacity; Execution is controlled control system 90A and speed change that speed change is delayed relatively delays control, thus initial stage of the urgent speed change of toroidal continuously variable transmission 1, from the ejection capacity transformation directive of pump-unit 92 is exported until through pump-unit 92 is during the actual total ejection flow that increases to main pump 96 and auxiliary pump 97 of the ejection flow of control system 90A ejection working oil, can prevent to require to a large amount of working oil of control system 90A supply.Consequently; At least the initial stage when the urgent speed change of toroidal continuously variable transmission 1 can prevent to require to a large amount of working oil of control system 90A supply the hydraulic pressure control device 9 of toroidal continuously variable transmission 1; Therefore; Can be suppressed at urgent speed change initial stage since the rising of the total ejection flow of the reality of the auxiliary pump 97 of main pump 96 take place to postpone to cause, with respect to working oil to the necessary flow working oil of control system 90A situation to the discharging jet quantity not sufficient of the reality of control system 90A, therefore can be according to the ejection capacity of suitably conversion working oil of running state.

Thus; When the hydraulic pressure control device 9 of this toroidal continuously variable transmission 1 can be suppressed at the urgent speed change of toroidal continuously variable transmission 1 with respect to the necessary flow working oil of the working oil among the control system 90A situation to the discharging jet quantity not sufficient of the reality of control system 90A; Therefore; For example; Can prevent to be supplied to the clamping pressure of the oil pressure pressing mechanism that constitutes control system 90A to produce the not enough situation of working oil of the 15a of hydraulic chamber, can prevent to be used for live roll 4 is clipped in the situation of the too small deficiency of clamping pressure between input disk 2 and the output disk 3.Thus; The hydraulic pressure control device 9 of this toroidal continuously variable transmission 1 through pump-unit 92 to the ejection capacity of control system 90A ejection working oil along with urgent speed change when relatively little capacity transforms to big relatively capacity; Can suppress to act on surface of contact on the contact segment of surface of contact 4a of

ring surface

2a, 3a and live roll 4 of input disk 2, output disk 3 and press lowly, make the situation that live roll 4 skids with respect to input torque to toroidal continuously variable transmission 1.

Here; Gear ratio control device 65 can be carried out through the gear ratio change portion 5 that constitutes control system 90A being controlled the speed change that the speed change speed that makes speed change reduces speed change is delayed relatively relatively and delay control, also can carry out through the gear ratio change portion 5 that constitutes control system 90A being controlled the speed change that the elapsed time point that makes speed change delays speed change is delayed relatively relatively to delay control.

Gear ratio control device 65 is when controlling the speed change speed (variable quantity of the time per unit of gear ratio (variance ratio)) that makes speed change and reduce to carry out speed change relatively and delay to control to the gear ratio change portion 5 that constitutes control system 90A; For example, make the speed change speed of speed change littler than the speed change speed in the common speed change.As stated; Gear ratio control device 65 calculates the target input speed based on calculation requirement driving force such as the accelerator opening or the speed of a motor vehicle and after calculating target output usually; And gear ratio change portion 5 controlled actual gear ratio, make that the actual input speed to 2 inputs of input disk becomes the target input speed.And; When gear ratio control device 65 delays to control in the execution speed change; For example, the variable quantity (variance ratio) that can calculate the input speed of time per unit delays control than the above-mentioned common little speed change of target input speed and uses the target input speed, and gear ratio change portion 5 is controlled gear ratio; Make actual input speed become above-mentioned speed change and delay control and use the target input speed, thereby the speed of verting of live roll 4 is reduced relatively and speed change speed is reduced relatively.

Gear ratio control device 65 is delaying to carry out under the situation that speed change delays to control through the gear ratio change portion 5 that constitutes control system 90A being controlled the elapsed time point that makes speed change relatively; For example, can control gear ratio change portion 5 makes the elapsed time point of speed change after the conversion concluding time of the ejection capacity of pump-unit 92 point.Promptly; In the case; Thereby gear ratio control device 65 is not controlled the actual urgent speed change of beginning to the gear ratio change portion 5 that constitutes control system 90A immediately after urgent speed change request is detected, thereby and can after the ejection flow of the actual total that increases to main pump 96 and auxiliary pump 97 of the ejection flow of control system 90A ejection working oil, control the urgent speed change that begins reality to the gear ratio change portion 5 that constitutes control system 90A through pump-unit 92.

Here, the conversion control device 66 of this mode of execution is controlled when speed change is delayed control system 90A at gear ratio control device 65 as stated, pump-unit 92 is controlled working oil is relatively increased to the conversion rate of the ejection capacity of control system 90A.That is, 66 pairs of transfer valve 98 of conversion control device are controlled the ejection destination that makes auxiliary pump 97 and are relatively increased to the conversion rate of control system 90A conversion from lubrication system 90B.

As stated; In transfer valve 98; Because of being supplied to solenoid 98a, the driving current of prearranging quatity acts on the active force that pressing force that the solenoid 98a on the not shown valve core of the spool valve produces produces greater than the elastic member 98b that acts on this valve core of the spool valve; Make valve core of the spool valve move to the ON position, the second ejection oil circuit 94d and control system ejection oil circuit 94e are in coupled condition, thereby the ejection destination of auxiliary pump 97 transforms to control system 90A from lubrication system 90B.Conversion control device 66 can improve the conversion responsiveness based on transfer valve 98 through making the travelling speed of valve core of the spool valve when the travelling speed of ON position side is higher than common conversion of this moment.That is, conversion control device 66 can improve the conversion responsiveness based on transfer valve 98 through setting greatly when common towards the pressing force on the valve core of the spool valve that acts on transfer valve 98 of ON position side.Conversion control device 66 is for example through be applied to the voltage on the solenoid 98a with comparing usually to increase, can increase the pressing force that the valve core of the spool valve based on solenoid 98a is moved to the ON position side.In addition; Thereby transfer valve 98 is for example pressed to the valve core of the spool valve effect under the big situation that makes the formation that valve core of the spool valve moves to the ON position of active force that the control oil pressure of ON position side and pressing force that this control oil pressure is produced produce than the elastic member 98b that acts on this valve core of the spool valve having based on pipeline; For example; Through increasing pipeline and press and increase the pressing force that acts on the control oil pressure on the valve core of the spool valve with comparing usually towards the ON position side; The travelling speed of valve core of the spool valve can be increased, conversion responsiveness can be improved based on transfer valve 98 to the ON position side.

Thus; The hydraulic pressure control device 9 of this toroidal continuously variable transmission 1 is controlled when speed change is delayed control system 90A at gear ratio control device 65 as stated; 66 pairs of pump-units 92 of conversion control device are controlled working oil are relatively increased to the conversion rate of the ejection capacity of control system 90A, therefore can shorten with working oil to the ejection state of control system 90A during based on the conversion to based on 2 ejection state transformations of main pump 96 and auxiliary pump 97 time of 1 ejection state of main pump 96.Therefore; The hydraulic pressure control device 9 of toroidal continuously variable transmission 1 can shorten working oil during the conversion of the ejection capacity of control system 90A; Thereby can shorten to control system 90A control make that speed change delays during; Therefore, for example, the generation of the so-called sluggishness (deterioration of responsiveness) that the down-shift and speed change (speed change request) etc. that can suppress with respect to be accompanied by acceleration request that the driver sends etc. postpones because of the responsiveness of the speed change of reality to cause.

Then, the conversion control to the ejection capacity of the pump-unit 92 of the hydraulic pressure control device 9 of toroidal continuously variable transmission 1 describes with reference to the sequential chart of the flow chart of Fig. 8 and Fig. 9.In Fig. 9, with the longitudinal axis be made as the transition state, target input speed (being equivalent to target change gear ratio) of the ejection capacity of accelerator opening, pump-unit 92, through the ejection flow of pump-unit 92 to control system 90A ejection working oil, transverse axis is made as time shaft.In addition, this control routine is with the extremely control cycle quilt execution times without number of tens of ms of separated number ms whenever.

At first, the conversion control device 66 of ECU60 obtains the temperature of current working oil based on the testing signal of working oil temperature sensor 58, and whether the temperature of judging current working oil is in predefined prespecified range (S100).In hydraulic pressure control device 9, the temperature of working oil than the low situation of predefined predetermined temperature under, work oil viscosity height makes working oil be difficult to flow, so working oil has the tendency that reduces relatively to the discharging jet measurer of control system 90A etc.In addition; In hydraulic pressure control device 9; The temperature of working oil than the high situation of predefined predetermined temperature under; The work oil viscosity is low to make working oil be easy to flow, but correspondingly the leakage rate of working oil from various gaps increases, so the pressure of the working oil of control system 90A etc. has the tendency that reduces relatively.Therefore; Conversion control device 66 is judged as (S100: not) under the situation outside predefined prespecified range in the temperature of working oil; Be described below, the driving of transfer valve 98 is controlled made through pump-unit 92 to the ejection state transformation of control system 90A ejection working oil to 2 ejection states.

Conversion control device 66 obtains current engine speed NE and judges that whether current engine speed NE is more than or equal to predefined engine speed NE1 (S102) based on the testing signal of engine rotation speed sensor 52 under the situation of temperature in predefined prespecified range of judging current working oil (S100: be).

Conversion control device 66 is being judged (S102: not) under the current situation of engine speed NE less than engine speed NE1; Obtain the speed of a motor vehicle of current vehicles 1A based on the testing signal of vehicle speed sensor 56, and whether the speed of a motor vehicle of judging current vehicles 1A is more than or equal to predefined preset vehicle speed (S104).

Conversion control device 66 is judged in S102 under the current situation of engine speed NE more than or equal to engine speed NE1 (S102: be); In S104, judge under the situation of the speed of a motor vehicle of current vehicles 1A (S104: be) more than or equal to preset vehicle speed; The driving of transfer valve 98 controlled make through pump-unit 92 to the ejection state transformation of control system 90A ejection working oil to 1 ejection state (S120; For example, the moment t1 of Fig. 9), gear ratio control device 65 delays speed change to control to identify to be set to closes (S122); Finish current control cycle, forward next control cycle to.In the case; Conversion control device 66 continues above-mentioned 1 ejection state under the situation that through pump-unit 92 to the ejection state of control system 90A ejection working oil is 1 ejection state originally in S120, and gear ratio control device 65 delays to control sign in speed change in S122 makes the above-mentioned continuation of closing under the situation of closing originally.Following explanation also is same.Consequently, the hydraulic pressure control device 9 of toroidal continuously variable transmission 1 will be set to relatively little capacity to the ejection capacity of control system 90A ejection working oil through pump-unit 92, can reduce the pump load (pump drives and loses) based on auxiliary pump 97 and improve oil consumption rate.

Conversion control device 66 is judged (S104: not), judge the urgent speed change request (S106) that has non-driver to send under the situation of the speed of a motor vehicle less than preset vehicle speed of current vehicles 1A in S104.Conversion control device 66 is for example based on the testing signal of various sensors or for control signal of the each several part of the vehicle 1A that comprises toroidal continuously variable transmission 1 etc.; Judge that the so-called down-shift and speed change have or not based on driver's accelerator pedal operation requires or have the gear shift operation etc. of indifferent manual mode, judges the urgent speed change request that has non-driver to send.

Conversion control device 66 is judging that whether the driver does not send under the situation of urgent speed change request (S106: be), judge based on pushing of clamping pressure control device 63 to increase control action (S108).Whether conversion control device 66 for example based on the testing signal of various sensors or for the control signal of the each several part of the vehicle 1A that comprises toroidal continuously variable transmission 1 etc., is judged based on pushing of clamping pressure control device 63 to increase control action.Increasing control based on pushing of clamping pressure control device 63 is the for example control carried out down of the unsteady state during tyre slip or during so-called ABS action etc., and is the control that increases than common running state through the cramping pressing force that clamping pressure control device 63 control oil pressure pressing mechanisms 15 are produced oil pressure pressing mechanism 15.When clamping pressure control device 63 was carried out pressing force increase control, then hydraulic pressure control device 9 was in working oil produces the more relatively state of necessary flow from the 15a of hydraulic chamber to the clamping pressure of the oil pressure pressing mechanism 15 that constitutes control system 90A.Therefore; Conversion control device 66 is judging that increasing control based on pushing of clamping pressure control device 63 is in (S108: not) under the situation in the action; Promptly; Be judged to be under the situation of astable operation state, be described below, the driving of transfer valve 98 is controlled made through pump-unit 92 to the ejection state transformation of control system 90A ejection working oil to 2 ejection states.

Conversion control device 66 increases control not (S108: be) under the situation of action judging based on pushing of clamping pressure control device 63, judge that whether instruction pressing force based on clamping pressure control device 63 is smaller or equal to predefined predetermined value (S110).Conversion control device 66 is for example based on the testing signal of various sensors or for the control signal of the each several part of the vehicle 1A that comprises toroidal continuously variable transmission 1 etc., judges that whether instruction pressing force based on clamping pressure control device 63 is smaller or equal to predefined predetermined value.Based on the instruction pressing force of clamping pressure control device 63 is for the command value (require cramping pressing force) of the oil pressure pressing mechanism 15 that produces the cramping pressing force from the cramping pressing force of clamping pressure control device 63 outputs, under the bigger unsteady state of the input torque of toroidal continuously variable transmission 1 input, be configured under the high load running state bigger than predefined predetermined value.If the instruction pressing force based on clamping pressure control device 63 is configured to the value greater than predefined predetermined value, hydraulic pressure control device 9 is in working oil produces the more relatively state of necessary flow from the 15a of hydraulic chamber to the clamping pressure of the oil pressure pressing mechanism 15 that constitutes control system 90A.Therefore; Conversion control device 66 is being judged (S110: not) under instruction pressing force based on clamping pressure control device 63 is than the big situation of predefined predetermined value; Promptly; Be judged to be under the situation of astable operation state, be described below, the driving of transfer valve 98 is controlled made through pump-unit 92 to the ejection state transformation of control system 90A ejection working oil to 2 ejection states.

Conversion control device 66 judges that whether instruction pressing force variable quantity based on clamping pressure control device 63 is smaller or equal to predefined prearranging quatity (S112) under judging based on the situation of instruction pressing force smaller or equal to predefined predetermined value of clamping pressure control device 63 (S110: be).Conversion control device 66 is for example based on the testing signal of various sensors or for the control signal of the each several part of the vehicle 1A that comprises toroidal continuously variable transmission 1 etc., judges that whether instruction pressing force variable quantity based on clamping pressure control device 63 is smaller or equal to predefined prearranging quatity.Based on the instruction pressing force variable quantity of clamping pressure control device 63 are the variable quantities (variance ratio) of time per unit of command value (requiring the cramping pressing force) that output to the cramping pressing force of the oil pressure pressing mechanism 15 that produces the cramping pressing force from clamping pressure control device 63.If greater than predefined prearranging quatity, hydraulic pressure control device 9 is in working oil produces the more relatively state of necessary flow from the 15a of hydraulic chamber to the clamping pressure of the oil pressure pressing mechanism 15 that constitutes control system 90A based on the instruction pressing force variable quantity of clamping pressure control device 63.Therefore; Conversion control device 66 is (S112: not) under the situation of instruction pressing force variable quantity greater than predefined prearranging quatity of judging based on clamping pressure control device 63; Promptly; Be judged to be under the situation of astable operation state, be described below, the driving of transfer valve 98 is controlled made through pump-unit 92 to the ejection state transformation of control system 90A ejection working oil to 2 ejection states.

Whether conversion control device 66 is judged based on the speed change of gear ratio control device 65 and is indicated flow smaller or equal to predefined predetermined amount of flow (S114) under judging based on the situation of instruction pressing force variable quantity smaller or equal to predefined prearranging quatity of clamping pressure control device 63 (S112: be).Conversion control device 66 is for example based on the testing signal of various sensors or for the control signal of the each several part of the vehicle 1A that comprises toroidal continuously variable transmission 1 etc., judges that whether speed change indication flow based on gear ratio control device 65 is smaller or equal to predefined predetermined amount of flow.Based on the speed change of gear ratio control device 65 indication flow be corresponding with the command value (requiring the speed Control pressing force) of the speed Control pressing force that outputs to the gear ratio change portion 5 that produces the speed Control pressing force from gear ratio control device 65, to the flow of the working oil of speed Control hydraulic chamber 82.If the predefined predetermined amount of flow of speed change indication flow-rate ratio based on gear ratio control device 65 is big, then hydraulic pressure control device 9 is in the necessary flow relatively more state of working oil to the speed Control hydraulic chamber 82 of the gear ratio change portion 5 that constitutes control system 90A.Therefore; Conversion control device 66 is being judged (S114: not) under the situation big based on the predefined predetermined amount of flow of speed change indication flow-rate ratio of gear ratio control device 65; Promptly; Be judged to be under the situation of astable operation state, be described below, the driving of transfer valve 98 is controlled made through pump-unit 92 to the ejection state transformation of control system 90A ejection working oil to 2 ejection states.

Conversion control device 66 judges based on the L/U joint transition control of torque-converters control device 61 whether carry out (S116) under judging based on the situation of speed change indication flow smaller or equal to predefined predetermined amount of flow of gear ratio control device 65 (S114: be).Conversion control device 66 is for example based on the testing signal of various sensors or for the control signal of the each several part of the vehicle 1A that comprises toroidal continuously variable transmission 1 etc., judges that L/U based on torque-converters control device 61 engages transition control and whether carries out.Engage in the engaging process of lock-up clutch that transition control is torque-converters 22 or the control of carrying out in the releasing process that engages based on the L/U of torque-converters control device 61.

Conversion control device 66 is judging that the L/U based on torque-converters control device 61 engages transition control just under executory situation (S116: be), directly stops current control cycle and does not transform to 1 ejection state, and forward next control cycle to.

On the other hand; Conversion control device 66 is not (S116: not), judge through pump-unit 92 and when the ejection state of control system 90A ejection working oil is 1 ejection state, pass through ejection flow that pump-unit 92 sprays working oil to the ejection flow of control system 90A ejection working oil, through from main pump 96 to control system 90A whether more than or equal to the necessary flow (S118) of the working oil among the current control system 90A under the situation about carrying out judging that L/U based on torque-converters control device 61 engages transition control.Conversion control device 66 is for example based on the testing signal of various sensors or for control signal of the each several part of the vehicle 1A that comprises toroidal continuously variable transmission 1 etc.; Acquisition through the working oil of main pump 96 in the ejection flow of control system 90A ejection working oil and current control system 90A necessary flow and compare, thereby judge that the ejection flow that sprays working oil to control system 90A through main pump 96 is whether more than or equal to the necessary flow of the working oil among the current control system 90A.Here; As stated, the necessary flow of the working oil among the control system 90A be and the gear ratio of toroidal continuously variable transmission 1 accordingly to the necessary flow of the working oil of speed Control hydraulic chamber 82, or and the surface of contact 4a of ring surface 2a, 3a and the live roll 4 of input disk 2, output disk 3 between surface of contact press accordingly the flow of the whole needed working oil of necessary flow dispatch control system 90A that clamping pressure is produced the working oil of the 15a of hydraulic chamber.

Conversion control device 66 judge through pump-unit 92 when the ejection state of control system 90A ejection working oil is 1 ejection state pass through pump-unit 92 to the ejection flow (through the ejection flow of main pump 96) of control system 90A ejection working oil to control system 90A ejection working oil less than the situation of the necessary flow of the working oil among the current control system 90A under (S118: deny); Directly stop current control cycle and be not transformed into 1 ejection state, and forward next control cycle to.

Conversion control device 66 through pump-unit 92 when the ejection state of control system 90A ejection working oil is 1 ejection state pass through pump-unit 92 to the ejection flow of control system 90A ejection working oil (spraying the ejection flow of working oil to control system 90A) through main pump 96 more than or equal to the situation of the necessary flow of the working oil among the current control system 90A under (S118: be); The driving of transfer valve 98 controlled make through pump-unit 92 to the ejection state transformation of control system 90A ejection working oil to 1 ejection state (S120; For example; The moment t1 of Fig. 9); Gear ratio control device 65 delays speed change to control to identify to be set to closes (S122), stops current control cycle and forwards next control cycle to.Consequently; Even engine speed NE is less than predetermined engine speed NE1; The hydraulic pressure control device 9 of toroidal continuously variable transmission 1 is under the situation near the state of steady operational status in the running state of the vehicle 1A that toroidal continuously variable transmission 1 is installed; Also be set to relatively little capacity through pump-unit 92 to the ejection capacity of control system 90A ejection working oil, can reduce also further to improve oil consumption rate based on the pump load (pump drives loss) of auxiliary pump 97.

Conversion control device 66 is judged (S100: not) under the situation of temperature outside predefined prespecified range of working oil in S100; Judge that in S106 the driver has (S106: not) under the situation of urgent speed change request; Judge that in S108 the increase of pushing based on clamping pressure control device 63 is controlled at (S108: not) under the situation in the action; In S110, judge (S110: not) under the situation of instruction pressing force based on clamping pressure control device 63 greater than predefined predetermined value; In S112, judge (S112: not) under the situation of instruction pressing force variable quantity based on clamping pressure control device 63 greater than predefined prearranging quatity; In S114, judge based on (S114: not) under the situation of speed change indication flow greater than predefined predetermined amount of flow of gear ratio control device 65; Thereby the running state of judging the vehicle 1A that toroidal continuously variable transmission 1 is installed is under the situation of astable operation state; The driving of transfer valve 98 controlled make through pump-unit 92 to the ejection state transformation of control system 90A ejection working oil to 2 ejection states (S124, for example, the moment t2 of Fig. 9).

And; Gear ratio control device 65 judges from the conversion elapsed time point of the ejection capacity of pump-unit 92, time point (for example, the moment t2 of Fig. 9) beginning of promptly having exported the transformation directive of ejection capacity from conversion control device 66 to pump-unit 92 whether pass through the predefined scheduled time (S126).

Gear ratio control device 65 is being judged under the situation that begins not pass through the predefined scheduled time from conversion control device 66 to the time point that pump-unit 92 has been exported the transformation directive of ejection capacity (S126: be); Promptly; Under the situation of ejection flow from pump-unit 92 to the ejection flow reality of control system 90A ejection working oil that judge the total that does not increase to main pump 96 and auxiliary pump 97 through; Speed change is delayed control sign be set to unlatching, carry out the gear ratio change portion 5 that constitutes control system 90A is controlled and speed change that speed change is delayed relatively delays control (S128).Consequently, the hydraulic pressure control device 9 of toroidal continuously variable transmission 1 can suppress that rising because of the total ejection flow of the reality of main pump 96 and auxiliary pump 97 takes place to postpone to cause, with respect to working oil to the necessary flow working oil of control system 90A situation to the discharging jet quantity not sufficient of the reality of control system 90A.

And the driving of 66 pairs of transfer valve 98 of conversion control device is controlled and is relatively increased through pump-unit 92 after the conversion rate of the ejection capacity of control system 90A (S130), stops current control cycle and forwards next control cycle to.Consequently, the hydraulic pressure control device 9 of toroidal continuously variable transmission 1 can shorten that speed change that speed change is delayed delays to control the term of execution and suppress the generation of sluggish (deterioration of responsiveness).

Gear ratio control device 65 is judged in S126 from conversion control device 66 and has been begun to pass through (S126: not) under the situation of the predefined scheduled time to the time point that pump-unit 92 has been exported the transformation directive of ejection capacity; Promptly; Through pump-unit 92 under the situation of the actual total ejection flow that increases to main pump 96 and auxiliary pump 97 of the ejection flow of control system 90A ejection working oil (for example; The moment t3 of Fig. 9); Speed change is delayed control sign be set to and close (S132), forward common speed Control to and stop current control cycle, and forward next control cycle to.

The hydraulic pressure control device 9 of the toroidal continuously variable transmission 1 that relates to according to the mode of execution of the present invention of above explanation; Can be from the input disk 2 of input side via as the live roll 4 of transferring elements output disk 3 transmission of drive force to outlet side; And the rotational speed that can infinitely change input disk 2 and output disk 3 is than being in the hydraulic pressure control device 9 of toroidal continuously variable transmission 1 of gear ratio; Comprise: pump-unit 92; This pump-unit can change the ejection capacity of working oil to control system 90A multistagely, and control system 90A presses and gear ratio through the surface of contact between pressure control input disk 2, output disk 3 and the live roll 4 of working oil; Gear ratio control device 65; Through pump-unit 92 to the ejection capacity of control system 90A ejection working oil along with speed change when relatively little capacity transforms to big relatively capacity, 65 couples of control system 90A of this gear ratio control device control speed change are relatively delayed.

In addition, according to the toroidal continuously variable transmission 1 that the mode of execution of the present invention of above explanation relates to, comprise above-mentioned hydraulic pressure control device 9 and the live roll 4 that constitutes transferring elements.

Therefore; This toroidal continuously variable transmission 1, hydraulic pressure control device 9 delay control when relatively little capacity transforms to big relatively capacity, control system 90A being controlled and carry out the speed change that relatively delays speed change along with speed change to the ejection capacity of control system 90A ejection working oil through pump-unit 92; Can suppress that rising because of the total ejection flow of the reality of the auxiliary pump 97 of main pump 96 takes place to postpone to cause, with respect to working oil to the necessary flow working oil of control system 90A situation to the discharging jet quantity not sufficient of the reality of control system 90A; Consequently, can be according to the ejection capacity of suitably conversion working oil of running state.

In addition; The toroidal continuously variable transmission 1, the hydraulic pressure control device 9 that relate to according to the mode of execution of the present invention of above explanation; Gear ratio control device 65 can through pump-unit 92 to the ejection capacity of control system 90A ejection working oil along with speed change when relatively little capacity transforms to big relatively capacity, control system 90A is controlled the speed change speed that makes speed change relatively descends.In the case, toroidal continuously variable transmission 1, hydraulic pressure control device 9 can be carried out and control relatively descend speed change that speed change is relatively delayed of the speed change speed that makes speed change through 65 couples of control system 90A of gear ratio control device and delay control.

In addition; The toroidal continuously variable transmission 1, the hydraulic pressure control device 9 that relate to according to the mode of execution of the present invention of above explanation; Gear ratio control device 65 can through pump-unit 92 to the ejection capacity of control system 90A ejection working oil along with speed change when relatively little capacity transforms to big relatively capacity, control system 90A is controlled the elapsed time point that makes speed change relatively delays.In the case, toroidal continuously variable transmission 1, hydraulic pressure control device 9 can be carried out and control the speed change that the elapsed time point that makes speed change relatively delays speed change is relatively delayed through 65 couples of control system 90A of gear ratio control device and delay control.

In addition; According to the toroidal continuously variable transmission 1 and hydraulic pressure control device 9 that the mode of execution of the present invention of above explanation relates to, gear ratio control device 65 begun to be transformed to from the conversion of the ejection capacity of pump-unit 92 to the ejection capacity of the reality of pump-unit 92 big relatively capacity during speed change is delayed.Therefore; Toroidal continuously variable transmission 1 and hydraulic pressure control device 9 output to pump-unit 92 to through pump-unit 92 is during the actual total ejection flow that increases to main pump 96 and auxiliary pump 97 of the ejection capacity of control system 90A ejection working oil at the transformation directive from the ejection capacity; Can prevent to require to a large amount of working oil of control system 90A supply, therefore can suppress reliably with respect to working oil to the necessary flow working oil of control system 90A situation to the actual discharging jet quantity not sufficient of control system 90A.

In addition; The toroidal continuously variable transmission 1 and hydraulic pressure control device 9 that relate to according to the mode of execution of the present invention of above explanation; Comprise conversion control device 66; When 65 couples of control system 90A of gear ratio control device control when speed change is delayed, 66 pairs of pump-units 92 of conversion control device are controlled and are relatively increased the conversion rate of working oil to the ejection capacity of control system 90A.Therefore; Toroidal continuously variable transmission 1 can shorten working oil during the conversion of the ejection capacity of control system 90A with hydraulic pressure control device 9; Thereby can shorten to control system 90A control make that speed change delays during, therefore can suppress the generation of sluggish (deterioration of responsiveness).

In addition, according to toroidal continuously variable transmission 1, hydraulic pressure control device 9 that the mode of execution of the present invention of above explanation relates to, pump-unit 92 has: to the main pump 96 of control system 90A ejection working oil; To control system 90A or be different from the auxiliary pump 97 of the lubrication system 90B ejection working oil of control system 90A; And can be between control system 90A and lubrication system 90B the transfer valve 98 of the ejection destination of the working oil of conversion auxiliary pump 97.Therefore; Transfer valve 98 transforms to any one among control system 90A and the lubrication system 90B with the ejection destination of the working oil in the auxiliary pump 97, and toroidal continuously variable transmission 1 can be with multistage (is 2 grades at this) mode conversion through the ejection capacity of pump-unit 92 to control system 90A ejection working oil with hydraulic pressure control device 9.

In addition; According to toroidal continuously variable transmission 1 and hydraulic pressure control device 9 that the mode of execution of the present invention of above explanation relates to, control system 90A is constituted as and comprises: through the gear ratio change portion 5 to the pressure change gear ratio of the working oil of speed Control hydraulic chamber 82 supplies; And the oil pressure pressing mechanism 15 that passes through the surface of contact pressure between pressure change input disk 2, output disk 3 and the live roll 4 of the working oil that the clamping pressure generation 15a of hydraulic chamber supplies.Therefore; Toroidal continuously variable transmission 1, hydraulic pressure control device 9 through pump-unit 92 to the ejection capacity of control system 90A ejection working oil along with speed change when relatively little capacity transforms to big relatively capacity; Execution is controlled control system 90A and the speed change that relatively delays speed change delays control, can suppress at least to produce the situation of the necessary flow working oil of the 15a of hydraulic chamber to the discharging jet quantity not sufficient of the reality of control system 90A with respect to working oil to the speed Control hydraulic chamber 82 of the gear ratio change portion 5 that constitutes control system 90A and the clamping pressure of oil pressure pressing mechanism 15.

In addition, the stepless speed variator that above-mentioned mode of execution of the present invention relates to is not limited to above-mentioned mode of execution, and can in the scope of claims record, carry out various changes.In above explanation, stepless speed variator is described to the toroidal continuously variable transmission of dual-chamber type, but is not limited thereto, and also can be the toroidal continuously variable transmission of single chamber type.

In addition, in above explanation, stepless speed variator of the present invention is described to toroidal continuously variable transmission 1, but is not limited thereto.

Figure 10 is a concise and to the point pie graph of using the variable v-belt drive of the hydraulic pressure control device that variation of the present invention relates to.In the explanation of above Fig. 1 to Fig. 9; Explained that the hydraulic pressure control device 9 as pressure medium control gear of the present invention is applied to the situation as the toroidal continuously variable transmission 1 of stepless speed variator; But be not limited thereto, stepless speed variator of the present invention also can be applicable to so-called variable v-belt drive 101 shown in figure 10.In addition, for formation, effect, effect common among this figure, omit the explanation and the identical symbol of mark of repetition with above-mentioned mode of execution as far as possible.

The variable v-belt drive 101 of the stepless speed variator that relates to as this variation of the present invention be can through as transferring elements with 104 from the rotary component of input side to the rotary component transmission of outlet side driving force from motor 21, and infinitely (continuously) rotating ratio of changing between the rotary component of rotary component and outlet side of input side is the so-called variable v-belt drive of gear ratio.That is, this variable v-belt drive 101 is constituted as and comprises: as the primary pulley 102 of the rotary component of input side, be passed to primary pulley 102 from the driving force of motor 21; As the secondary pulley 103 of the rotary component of outlet side, change the driving force and the output that are delivered to primary pulley 102; And as transferring elements be with 104, with 104 will be delivered to primary pulley 102 driving force transmit to secondary pulley 103.In addition, this variable v-belt drive 101 is constituted as and comprises: the ECU60 that the each several part of the each several part of motor 21 and variable v-belt drive 101 is controlled; And as the hydraulic pressure control device 9 of the pressure medium control gear that the oil pressure of each several part is controlled.

In addition, in following explanation, the formation of motor 21, torque-converters 22, forward-reverse shifting mechanism 23, power transmission mechanism 24, differential gear 25 etc. and above-mentioned toroidal continuously variable transmission 1 are roughly the same, so omit explanation.In addition; The ECU60 of ECU60 of this variation and mode of execution 1 (with reference to Fig. 1) likewise; Be constituted as and comprise torque-converters control device 61, forward-reverse conversion control device 62, clamping pressure control device 63, engine control portion 64, gear ratio control device 65, conversion control device 66, omit their diagram at this.In addition, the hydraulic pressure control device 9 of the hydraulic pressure control device of this variation 9 and mode of execution 1 (with reference to Fig. 1) likewise is constituted as and comprises the pump-unit 92 (with reference to Fig. 1) that spray capacity variable type, in this their diagram of omission.

Variable v-belt drive 101 is constituted as and comprises: as primary pulley axle 121, the secondary pulley axle 131 of two belt shafts that dispose with predetermined spaced and parallel; Primary fixed pulley 122, secondary fixed pulley 132, elementary movable sheave 123, secondary movable sheave 133, be with 104.Elementary movable sheave 123 is configured in respectively on primary pulley axle 121 and the secondary pulley axle 131 with secondary movable sheave 133, and can on primary pulley axle 121 and secondary pulley axle 131, slide along axial direction.Primary fixed pulley 122 and secondary fixed pulley 132 respectively with this elementary movable sheave 123, secondary movable sheave 133 relatively and be configured on primary pulley axle 121, the secondary pulley axle 131, and and elementary movable sheave 123, secondary movable sheave 133 between form elementary groove 127 and secondary slot 137.Be wrapped in the elementary groove of in the elementary movable sheave of each of relative configuration 123, secondary movable sheave 133 and primary fixed pulley 122, the secondary fixed pulley 132 each 127, the secondary slot 137 with 104.

Particularly, as stated, variable v-belt drive 101 comprises primary pulley 102 as a belt wheel, as the secondary pulley 103 of another belt wheel, be with 104, ECU60, hydraulic pressure control device 9.

Primary pulley 102 is belt wheels, and through transmitting the engine torque that transmits via forward-reverse shifting mechanism 23 with 104 to the secondary pulley 103 as another belt wheel.In other words, be transfused to wherein primary pulley 102 from the engine torque (driving force) of motor 21 (driving source) and constitute a belt wheel in two included belt wheels of variable v-belt drive 101.

Primary pulley 102 comprises primary pulley axle 121, primary fixed pulley 122, elementary movable sheave 123 and constitutes through making primary pulley 102 produce the elementary hydraulic chamber 124 as the speed Control pressure chamber that the strap clamp pressure change the gear ratio of variable v-belt drive 101.

Primary pulley axle 121 is rotatably mounted by bearing part 125,126.In addition, primary pulley axle 121 has not shown working oil path in inside.The working oil path is connected with the oil pressure control loop of hydraulic pressure control device 9, and is supplied to the working oil of elementary hydraulic chamber 124 to flow into the working oil path from hydraulic pressure control device 9.

It is tabular that primary fixed pulley 122 forms circular cone, and be set on the position relative with elementary movable sheave 123, rotate integratedly with primary pulley axle 121.Here, primary fixed pulley 122 forms the annulus of giving prominence to radial outside from the periphery of primary pulley axle 121.That is, primary fixed pulley 122 is provided with the periphery of primary pulley axle 121 integratedly.In addition, primary fixed pulley 122 also can be arranged with the primary pulley axle in 121 minutes.

It is tabular that elementary movable sheave 123 forms circular cone, for example, chimeric moving vertically and can be supported with the mode of primary pulley axle 121 one rotation with respect to primary pulley axle 121 through spline.

Primary fixed pulley 122 and elementary movable sheave 123 are formed with the elementary groove 127 of V font between face relative face of movable sheave primary fixed pulley 122 and elementary 123 and elementary movable sheave 123 and that primary fixed pulley 122 is relative.Elementary groove 127 is wound with endless band 104.That is, be with 104 to be set to be clipped between primary fixed pulley 122 and the elementary movable sheave 123.

Elementary hydraulic chamber 124 comprises elementary movable sheave cramping pressing force acting surface 123a and the primary piston 128 that is fixed to the ring-type of primary pulley axle 121, and elementary movable sheave cramping pressing force acting surface 123a is as the pressure acting surface at the back side of the opposition side of the face relative with primary fixed pulley 122 of elementary movable sheave 123.On the elementary movable sheave cramping pressing force acting surface 123a of elementary movable sheave 123, be formed with outstanding to an axial direction, promptly to the outstanding protuberance 123b cylindraceous of primary fixed pulley 122 opposition sides.For example between protuberance 123b and primary piston 128, being provided with, not shown elementary hydraulic chamber such as seal ring uses sealed member.That is, constitute between elementary movable sheave cramping pressing force acting surface 123a and the primary piston 128 of elementary movable sheave 123 of elementary hydraulic chamber 124 and seal by sealed member.In addition, bearing part 126 and primary piston 128 are fixed to primary pulley axle 121 through locking nut 129.

Working oil in the not shown working oil path of inflow primary pulley axle 121 is supplied to elementary hydraulic chamber 124.That is, hydraulic pressure control device 9 is to elementary hydraulic chamber 124 supply working oil, and through the oil pressure of elementary hydraulic chamber 124 elementary movable sheave 123 slided vertically, and make elementary movable sheave 123 with respect to primary fixed pulley 122 approaching or away from.Elementary hydraulic chamber 124 acts on elementary movable sheave cramping pressing force acting surface 123a through the movable sheave pressing force that the working oil that is supplied to elementary hydraulic chamber 124 will make elementary movable sheave 123 push to primary fixed pulley 122 sides axially, produce for be wrapped in the elementary groove 127 with 104 strap clamp pressure.That is, the oil pressure of primary pulley 102 through elementary hydraulic chamber 124 be to being with 104 to produce the strap clamp pressure, and through the elementary movable sheave 123 of strap clamp pressure change that the produces axle direction position with respect to primary fixed pulley 122.Thus, elementary hydraulic chamber 124 for example has the function of the change gear that changes variable v-belt drive 101.

Promptly; The primary pulley 102 of this mode of execution is equivalent to the rotary component of input side of the present invention, and is equivalent to through changing the unit to the gear ratio of the present invention as the pressure change gear ratio of the working oil of the elementary hydraulic chamber of speed Control pressure chamber 124 supplies.

In addition; Secondary pulley 103 is another belt wheels; And through with 104 will be delivered to primary pulley 102 engine torque to not shown reduction drive gear transmission, and transmit these torques to driving wheel 27 via power transmission mechanism 24, differential gear 25, transmission shaft 26.In other words, output to wherein secondary pulley 103 from the driving force of primary pulley 102 and constitute another belt wheel in two included belt wheels of variable v-belt drive 101.

Secondary pulley 103 comprises secondary pulley axle 131, secondary fixed pulley 132, secondary movable sheave 133 and as the secondary hydraulic chamber 134 of surface of contact pressure-controlled pressure chamber; Secondary hydraulic chamber 134 adjusts the tension force with 104 through making secondary pulley 103 produce the strap clamp pressure, and changes primary fixed pulley 122, secondary fixed pulley 132, elementary movable sheave 123, secondary movable sheave 133 and press with 104 surface of contact according to input torque.

Secondary pulley axle 131 is rotatably mounted by bearing part 135,136.In addition, secondary pulley axle 131 has not shown working oil path in inside.The working oil path is connected with hydraulic pressure control device 9, and flows into the working oil path from the working oil of hydraulic pressure control device 9 to 134 supplies of secondary hydraulic chamber.

Above-mentioned primary pulley axle 121 is configured to mutual almost parallel with secondary pulley axle 131.

It is tabular that secondary fixed pulley 132 forms circular cone, and be set on the position relative with secondary movable sheave 133, rotate integratedly with secondary pulley axle 131.Here, secondary fixed pulley 132 forms the annulus of giving prominence to radial outside from the periphery of secondary pulley axle 131.That is, in variation, secondary fixed pulley 132 is provided with the periphery of secondary pulley axle 131 integratedly.In addition, secondary fixed pulley 132 also can be arranged with the secondary pulley axle in 131 minutes.

It is tabular that secondary movable sheave 133 forms circular cone, for example, chimeric moving vertically and can be supported with the mode of secondary pulley axle 131 one rotation with respect to secondary pulley axle 131 through spline.

Secondary fixed pulley 132 and secondary movable sheave 133 are formed with the secondary slot 137 of V-shape between face relative face of movable sheave secondary fixed pulley 132 and secondary 133 and secondary movable sheave 133 and that secondary fixed pulley 132 is relative.Secondary slot 137 is wound with endless band 104.That is, be with 104 to be set to be clipped between secondary fixed pulley 132 and the secondary movable sheave 133.

The secondary movable sheave cramping pressing force acting surface 133a at the back side of the opposition side of the face relative that secondary hydraulic chamber 134 comprises secondary movable sheave 133 and the secondary piston 138 that is fixed to the ring-type of secondary pulley axle 131 with secondary fixed pulley 132.Be formed with on the secondary movable sheave cramping pressing force acting surface 133a of secondary movable sheave 133 axially a direction outstanding, promptly to the protuberance 133b of the outstanding drum of the opposition side of secondary fixed pulley 132.For example be provided with not shown secondary hydraulic chamber such as seal ring between protuberance 133b and the secondary piston 138 and use sealed member.That is the secondary movable sheave cramping pressing force acting surface 133a and the secondary piston 138 that, constitute the secondary movable sheave 133 of secondary hydraulic chamber 134 are sealed by sealed member.In addition, bearing part 135 and secondary piston 138 are fixed to secondary pulley axle 131 through locking nut 139b.In addition, bearing part 136 is fixed to secondary pulley axle 131 through locking nut 139a.In addition, between this bearing part 136 and secondary fixed pulley 132, be provided with Parking gear 108.

Working oil in the not shown working oil path of inflow secondary pulley axle 131 is supplied to secondary hydraulic chamber 134.That is, hydraulic pressure control device 9 is to secondary hydraulic chamber 134 supply working oil, and through the oil pressure of secondary hydraulic chamber 134 secondary movable sheave 133 slided vertically, and make secondary movable sheave 133 with respect to secondary fixed pulley 132 approaching or away from.The movable sheave pressing force that the secondary fixed pulley side that secondary hydraulic chamber 134 will make secondary movable sheave 133 axially go up through the working oil that is supplied to secondary hydraulic chamber 134 is pushed acts on secondary movable sheave cramping pressing force acting surface 133a, produce for be wrapped in the secondary slot 137 with 104 strap clamp pressure.That is, the oil pressure of secondary pulley 103 through secondary hydraulic chamber 134 be to being with 104 to produce the strap clamp pressure, and through the secondary movable sheave 133 of strap clamp pressure change that the produces axle direction position with respect to secondary fixed pulley 132.Thus, secondary hydraulic chamber 134 for example bears through control and keeps with the 104 certain part of functions of contact radius with respect to primary pulley 102 and secondary pulley 103 with 104 tension force.

Promptly; The secondary pulley 103 of this mode of execution is equivalent to the rotary component of outlet side of the present invention; And be equivalent to surface of contact of the present invention and press and change the unit, surface of contact of the present invention is pressed and is changed the unit and press with the surface of contact with 104 through change primary fixed pulley 122, secondary fixed pulley 132, elementary movable sheave 123, secondary movable sheave 133 to the pressure as the working oil of secondary hydraulic chamber 134 supplies of surface of contact pressure-controlled pressure chamber.

With 104 to secondary pulley 103 transmit from as the motor 21 (driving source) of input side to the driving force of primary pulley 102 inputs, be engine torque.Be wrapped between the secondary slot 137 of elementary groove 127 and secondary pulley 103 of primary pulley 102 with 104.In addition, are the endless bands that constitute by a plurality of metal band members and a plurality of steel ring with 104.

Thereby ECU60 is actual gear ratio according to the running state (travelling state) that the vehicle of variable v-belt drive 101 is installed to the gear ratio of the reality of the driving control variable v-belt drive 101 of the each several part of variable v-belt drive 101.ECU60 based on various sensor to running statees such as engine speed, throttle valve opening, accelerator opening, engine speed, input speed, output speed, gear wait to confirm that the gear ratio of target is a target change gear ratio, and carry out oil pressure and control the oil pressure of adjusting elementary hydraulic chamber 124 and the oil pressure of secondary hydraulic chamber 134 through driving hydraulic pressure control device 9.Promptly; ECU60 is through carrying out dutycycle control based on control command value to the driving current of the not shown flow control valve that is supplied to hydraulic pressure control device 9; Adjust the oil pressure of elementary hydraulic chamber 124 and the oil pressure of secondary hydraulic chamber 134, make elementary movable sheave 123, secondary movable sheave 133 with respect to primary fixed pulley 122, secondary fixed pulley 132 near and away from.And; ECU60 through make elementary movable sheave 123, secondary movable sheave 133 with respect to primary fixed pulley 122, secondary fixed pulley 132 near and away from; Can adjust strap clamp pressure and the strap clamp pressure in the secondary pulley 103 in the primary pulley 102 and control change gear; Thereby can the actual gear ratio as the gear ratio of reality be controlled to be the target change gear ratio as the gear ratio of target, change gear is as the input speed of the rotating speed of primary pulley 102 and ratio as the output speed of the rotating speed of secondary pulley 103.

Here; The control system 90A of this variation is constituted as and comprises: change the primary pulley 102 of unit as gear ratio of the present invention, primary pulley 102 is through changing gear ratio to the pressure as the working oil of elementary hydraulic chamber 124 supplies of speed Control pressure chamber; And press the secondary pulley 103 that changes the unit as surface of contact of the present invention, secondary pulley 103 is pressed with the surface of contact with 104 through change primary fixed pulley 122, secondary fixed pulley 132, elementary movable sheave 123, secondary movable sheave 133 to the pressure as the working oil of secondary hydraulic chamber 134 supplies of surface of contact pressure-controlled pressure chamber.In the case, in secondary pulley 103, for example, secondary fixed pulley 132 is equivalent to be used to make clamping pressure to act on the 1st cramping parts with 104, and secondary movable sheave 133 is equivalent to be used to make clamping pressure to act on the 2nd cramping parts with 104.In addition, gear ratio changes the unit and the surface of contact relation between the change unit of pressing can be opposite, that is, also can primary pulley 102 be pressed as surface of contact to change the unit, and secondary pulley 103 is changed the unit as gear ratio.

In addition, the lubrication system 90B as supply system that is different from the control system 90A of this variation is constituted as and comprises: the sliding parts (part that spline is chimeric) of primary pulley axle 121 and elementary movable sheave 123; The sliding parts (part that spline is chimeric) of secondary pulley axle 131 and secondary movable sheave 133; Bearing part 125,126,135,136; The working oil path that is communicated with them etc.

And; In the variable v-belt drive 101 that constitutes as stated; Likewise; Variable v-belt drive 101 and hydraulic pressure control device 9 through pump-unit 92 to the ejection capacity of control system 90A ejection working oil along with speed change when relatively little capacity transforms to big relatively capacity; Execution is controlled control system 90A and speed change that speed change is delayed relatively delays control; Thereby can suppress that rising because of the total ejection flow of the reality of main pump 96 and auxiliary pump 97 delays to cause, with respect to working oil to the necessary flow working oil of control system 90A situation to the discharging jet quantity not sufficient of the reality of control system 90A, consequently, can be according to the ejection capacity of suitably conversion working oil of running state.Thus; This variable v-belt drive 101 and hydraulic pressure control device 9 through pump-unit 92 to the ejection capacity of control system 90A ejection working oil along with urgent speed change when relatively little capacity transforms to big relatively capacity, can prevent primary fixed pulley 122, secondary fixed pulley 132, elementary movable sheave 123, secondary movable sheave 133 and press with 104 surface of contact with respect to the input torque low situation of skidding that makes that became with 104.

Applicability on the industry

As stated; The pressure medium control gear of the stepless speed variator that the present invention relates to and stepless speed variator can suitably change the ejection capacity of working medium according to running state, and preferably be applied to the corresponding optimum condition of the travelling state of vehicle under will be delivered to the pressure medium control gear and the stepless speed variator of the stepless speed variator on road surface from driving force as the internal-combustion engine of driving source or motor.

Claims

1. the pressure medium control gear of a stepless speed variator; Said stepless speed variator can pass to from the rotary component of input side driving force the rotary component of outlet side via transferring elements; And can infinitely change gear ratio; Said gear ratio is the said rotary component of input side and the rotational speed ratio of the said rotary component of outlet side, and said pressure medium control gear is characterised in that, comprising:

Pump unit, said pump unit can multistage ground conversion working medium to the ejection capacity of control system, the surface of contact that said control system is controlled between said rotary component and the said transferring elements through the pressure of said working medium is pressed and said gear ratio; And

The gear ratio control unit; When the ejection capacity that sprays said working medium to said control system through said pump unit along with speed change when relatively little capacity transforms to big relatively capacity, said gear ratio control unit is controlled said control system and said speed change is relatively delayed.

2. the pressure medium control gear of stepless speed variator according to claim 1, wherein,

When the ejection capacity that sprays said working medium to said control system through said pump unit along with speed change when relatively little capacity transforms to big relatively capacity, said gear ratio control unit is controlled said control system and the speed change speed of said speed change is relatively descended.

3. the pressure medium control gear of stepless speed variator according to claim 1, wherein,

When the ejection capacity that sprays said working medium to said control system through said pump unit along with speed change when relatively little capacity transforms to big relatively capacity, said gear ratio control unit is controlled said control system and the elapsed time point of said speed change is relatively delayed.

4. the pressure medium control gear of stepless speed variator according to claim 1; Wherein, Said gear ratio control unit begun to transform to from the conversion of the ejection capacity of said pump unit to the ejection capacity of the reality of said pump unit said big relatively capacity during, said speed change is delayed.

5. the pressure medium control gear of stepless speed variator according to claim 1, wherein,

Comprise the conversion control unit; When said gear ratio control unit was controlled said control system and said speed change is delayed, said conversion control unit was controlled said pump unit and is relatively increased the conversion rate of said working medium to the ejection capacity of said control system.

6. the pressure medium control gear of stepless speed variator according to claim 1, wherein,

Said pump unit has: first pump, and said first pump sprays said working medium to said control system; Second pump, said second pump sprays said working medium to the supply system that said control system perhaps is different from said control system; And converter unit, said converter unit can be between said control system and said supply system the ejection destination of the said working medium in said second pump of conversion.

7. the pressure medium control gear of stepless speed variator according to claim 1, wherein,

Said control system comprises: gear ratio changes the unit, and the pressure that said gear ratio changes the said working medium of unit through being supplied to the speed Control pressure chamber changes said gear ratio; And surface of contact press to change the unit, and said surface of contact is pressed the pressure that changes the said working medium of unit through being supplied to surface of contact pressure-controlled pressure chamber to change said surface of contact and pressed.

8. a stepless speed variator is characterized in that, comprising:

The pressure medium control gear of stepless speed variator according to claim 1; And

Constitute the live roll of said transferring elements.

9. a stepless speed variator is characterized in that, comprising:

Constitute the band of said transferring elements.